US10119738B2 - Air conditioning system with vapor injection compressor - Google Patents
Air conditioning system with vapor injection compressor Download PDFInfo
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- US10119738B2 US10119738B2 US14/862,762 US201514862762A US10119738B2 US 10119738 B2 US10119738 B2 US 10119738B2 US 201514862762 A US201514862762 A US 201514862762A US 10119738 B2 US10119738 B2 US 10119738B2
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/003—Indoor unit with water as a heat sink or heat source
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/004—Outdoor unit with water as a heat sink or heat source
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/029—Control issues
- F25B2313/0292—Control issues related to reversing valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0311—Pressure sensors near the expansion valve
-
- F25B2341/065—
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
-
- Y02B30/72—
-
- Y02B30/741—
Definitions
- the present disclosure relates to air conditioning systems and, in particular, to efficient-enhanced reversible air conditioning systems capable of both heating and refrigeration.
- Heating and cooling systems may include a compressor for compressing a working refrigerant fluid, a condenser heat exchanger for extracting heat from the refrigerant fluid, an expansion valve, and an evaporator heat exchanger for extracting heat from an external source.
- refrigeration systems may further include an economizer heat exchanger and/or a vapor injection feature associated with the compressor for increasing both the capacity and the efficiency of the compressor.
- the refrigerant is a high pressure hot liquid upon leaving the compressor, is a high pressure warm liquid downstream of the condenser, is a low pressure warm gas downstream of the expansion valve, and is a low pressure cool gas downstream of the evaporator.
- An economizer may be used to further influence the thermal state of the refrigerant between the condenser and evaporator.
- An auxiliary refrigerant flow is tapped from the main refrigerant flow downstream of the economizer heat exchanger and passed through an expansion valve to expand the auxiliary refrigerant flow before same is passed back through the economizer heat exchanger in heat exchange relation with the main refrigerant flow. This serves to further subcool the main refrigerant flow upstream of the evaporator.
- the economizer heat exchanger also discharges an auxiliary refrigerant flow in the form of an intermediate pressure vapor, which is then injected into the compressor.
- an intermediate pressure vapor which is then injected into the compressor.
- a scroll compressor is used in connection with such a system, and the vapor is injected at an intermediate pressure location within the wraps of the scroll compressor.
- the present disclosure provides an air conditioning system which can be toggled between a heating mode, in which heat is withdrawn from a source (e.g., a geothermal source) and deposited into a conditioned space (e.g., a building), and a cooling mode, in which heat is withdrawn from the conditioned space and deposited into the source.
- the air conditioning system uses a combination of efficiency-enhancing technologies, including injection of superheated vapor into the system's compressor from an economizer circuit, adjustable compressor speed, the use of one or more coaxial heat exchangers and the use of electronic expansion valves that are continuously adjustable from a fully closed to various open positions.
- a controller may be used to control the system for optimal performance in both the heating and cooling modes, such as by disabling the economizer circuit and vapor injection when the system is in the cooling mode.
- FIG. 1 is a schematic illustration of an air conditioning system in accordance with the present disclosure, illustrating refrigerant flow in a heating mode
- FIG. 2 is another schematic illustration of the air conditioning system shown in FIG. 1 , with refrigerant flow reversed for a cooling mode;
- FIG. 3 is an elevation view of a scroll compressor including vapor injection in accordance with the present disclosure
- FIG. 4 is a perspective view of a coaxial heat exchanger used in the air conditioning system shown in FIG. 1 ;
- FIG. 5 is an elevation, cross-sectional view of a portion of the coaxial heat exchanger shown in FIG. 4 , illustrating fluid flow therethrough;
- FIG. 6 is an elevation, cross-section view of a flash tank used in some air conditioning systems for separating entrained liquid from vapor;
- FIG. 7 is a schematic view of a geothermal air conditioning system in accordance with the present disclosure.
- air conditioning refers to both heating and cooling a conditioned space (e.g., the inside of a building).
- a conditioned space e.g., the inside of a building.
- an air conditioning system may be reversible to cool a conditioned space while exhausting heat to a source (e.g., a geothermal source), or to heat a conditioned space by extracting heat from the source.
- a source e.g., a geothermal source
- “superheated vapor” refers to a vapor whose temperature is measurably above its liquid/vapor phase change temperature for a given vapor pressure.
- subcooled liquid refers to a liquid whose temperature is measurably below its liquid/vapor phase change temperature for a given ambient vapor pressure.
- vapor mixture refers to mixed liquid-and-vapor phase fluid in which the fluid can undergo phase changes (i.e., from liquid to saturated vapor or from saturated vapor to liquid) at constant pressure and temperature.
- the present disclosure provides air conditioning system 10 which is reconfigurable between a heating mode ( FIG. 1 ) and a cooling mode ( FIG. 2 ).
- Such reconfiguration may be accomplished by actuation of a four way reversing valve 14 , which reverses the direction of refrigerant flow among the various components of system 10 , thereby reversing the flow of heat to and from a source S (e.g., a geothermal source) and a load B (e.g., the interior of a building or other thermally conditioned space).
- a source S e.g., a geothermal source
- load B e.g., the interior of a building or other thermally conditioned space
- System 10 may further include an economizer heat exchanger 20 which enables a vapor injection feature to enhance the efficiency and function of the compressor 12 in the heating mode, but may not be needed in the cooling mode.
- an economizer heat exchanger 20 which enables a vapor injection feature to enhance the efficiency and function of the compressor 12 in the heating mode, but may not be needed in the cooling mode.
- the toggling of reversing valve 14 from the heating mode to the cooling mode may be accompanied by adjusting an economizer expansion valve 24 to cease refrigerant flow therethrough, effectively disabling the vapor injection in the cooling mode.
- System 10 includes compressor 12 fluidly connected to load heat exchanger 16 and source heat exchanger 18 via reversing valve 14 . Operably interposed between load heat exchanger 16 and source heat exchanger 18 is economizer heat exchanger 20 .
- Primary expansion valve 22 is operably interposed between economizer 20 and source heat exchanger 18 , while economizer expansion valve 24 selectively receives a portion of the refrigerant flow and discharges to economizer 20 in the heating mode.
- economizer expansion valve 24 prevents one of the two flows of refrigerant through economizer heat exchanger 20 , effectively nullifying the effect of economizer 20 on the thermal characteristics of air conditioning system 10 , as also described in detail below.
- Air conditioning system 10 is configured as a reversible heat pump.
- refrigerant flow through system 10 sends hot refrigerant through load heat exchanger 16 , which operates as a condenser depositing heat Q 1 into a conditioned space B, while cold refrigerant is sent through a source heat exchanger 18 which operates as an evaporator to withdraws heat Q 3 from a source S, e.g., a geothermal source.
- load heat exchanger 16 operates as an evaporator and source heat exchanger 18 operates as a condenser.
- FIG. 1 illustrates air conditioning system 10 in the heating mode.
- Compressor 12 receives refrigerant in a low-pressure superheated vapor phase at compressor inlet 30 and vapor injection inlet 32 , as described below, and compresses this refrigerant vapor into a high pressure, superheated vapor phase thereby increasing the temperature, enthalpy and pressure of the refrigerant.
- This hot vapor phase refrigerant discharges at compressor outlet 28 into fluid line 34 , which conveys the vapor to reversing valve 14 .
- Valve 14 passes this superheated vapor to fluid line 36 , which conveys the vapor to the compressor-side port 38 of load heat exchanger 16 .
- Load heat exchanger 16 is in thermal communication with a conditioned space B, which may be a residence or other building, for example, and operates to exchange heat Q 1 between the refrigerant and a working fluid and thereby send heat Q 1 to conditioned space B.
- a conditioned space B which may be a residence or other building, for example
- the superheated refrigerant vapor received at port 38 discharges heat Q 1 to a relatively cooler working fluid circulating through working fluid lines 42 between building B and load heat exchanger 16 .
- the heated working fluid exits at crossflow outlet 38 A of load heat exchanger 16 , carrying heat Q 1 which is subsequently deposited in building B.
- building B may have a radiant heat system which extracts heat Q 1 from the working fluid and then sends cooled fluid back to crossflow inlet 40 A of load heat exchanger 16 , where the working fluid is again allowed to circulate through heat exchanger 16 to absorb heat Q 1 from the hot refrigerant vapor.
- Other heating systems for building B may be used in accordance with the present disclosure, such as forced-air heating systems or any other suitable heat transfer arrangement.
- the refrigerant may transfer heat to a circulating working fluid which deposits heat in building B, or warmed working fluid may itself be deposited into building B directly, such as hot water being directed into a hot water heater for consumption in building B, direct refrigerant-to-air heat transfer (e.g., by blowing air over hot heat exchanger coils into building B), and the like.
- the removal of heat Q 1 from the refrigerant as it passes through load heat exchanger 16 effects a phase change from superheated vapor (at the compressor-side port 38 ) to a partially subcooled liquid (at economizer-side port 40 ), which is discharged to fluid line 44 and conveyed to the load-side port 46 of economizer heat exchanger 20 .
- the refrigerant flows through heat exchanger 20 , which removes heat Q 2 therefrom as described below.
- the full volume of refrigerant flow passes through fluid line 50 A to fluid divider 51 , where a main flow of refrigerant continues toward source heat exchanger 18 via fluid line 50 B, while a portion of the refrigerant is diverted into fluid line 52 A and flows toward economizer expansion valve 24 .
- subcooled liquid refrigerant is allowed to expand into a low-pressure, cool liquid- and vapor mixed-phase state.
- Pressure sensing line 54 A is fluidly connected to expansion valve 24 , such that the pressure within valve 24 can be monitored remotely, e.g., by controller 70 (further described below).
- the low-pressure, mixed-phase refrigerant discharged from valve 24 is transmitted through fluid line 52 B to a crossflow inlet 48 A of economizer 20 where it circulates in heat-transfer relationship with the main refrigerant flow until reaching crossflow outlet 46 A.
- heat Q 2 transfers from the warmer main flow of liquid refrigerant passing from port 46 to port 48 to the low-pressure flow of the economizer portion of refrigerant, such that the refrigerant is warmed to a low-pressure superheated vapor by the time it discharges at outlet 46 A.
- This superheated vapor is carried by vapor injection fluid line 54 B to vapor injection inlet 32 of compressor 12 .
- the transfer of heat Q 2 also serves to further lower the temperature of the subcooled liquid phase refrigerant exiting the source-side port 48 , as compared to the liquid phase refrigerant entering at the load-side port 46 .
- a main flow of this lower-temperature subcooled liquid phase refrigerant passes divider 51 and flows through fluid line 50 B to primary expansion valve 22 .
- valve 22 the sub-cooled liquid is allowed to expand into a low-pressure, cold, mixed liquid/vapor phase.
- This cold fluid is conveyed via fluid line 56 A to a filter/dryer 26 , which separates entrained liquid from the vapor and discharges the cold liquid and vapor to fluid line 56 B, which conveys the refrigerant to the economizer-side port 60 of source heat exchanger 18 .
- the cold mixed-phase refrigerant received at economizer-side port 60 passes through source heat exchanger 18 , receiving heat Q 3 from working fluid circulating through source heat exchanger 18 from source S, thereby warming up to a low-pressure, superheated vapor phase refrigerant which is discharged at the valve-side port 62 .
- Source S may be, for example, a geothermal source which is at a consistently warmer temperature than the cold refrigerant received at the economizer-side port 60 .
- Cooled working fluid is circulated from crossflow outlet 60 A, through working fluid lines 64 circulating through source S where the working fluid is warmed, and back to source heat exchanger 18 at crossflow inlet 62 A. The warmed working fluid is then ready to discharge heat Q 3 to the cold refrigerant as noted above.
- the working fluid circulating through load heat exchanger 16 may be, e.g., water
- the working fluid circulating through source heat exchanger 18 may be, e.g., water, methanol, propylene glycol, or ethylene glycol.
- the low-pressure, superheated vapor discharged from the valve-side port 62 of source heat exchanger 18 is conveyed via fluid line 66 to reversing valve 14 , where it is allowed to pass to fluid line 68 , which in turn conveys the vapor to compressor inlet 30 to be compressed for the next refrigerant cycle.
- FIG. 2 a cooling mode of air conditioning system 10 is illustrated in which refrigerant flow is substantially reversed from the heating mode of FIG. 1 , and the discharge of heated vapor from economizer 20 to compressor 12 is ceased such that vapor injection functionality is operably disabled.
- 4-way reversing valve 14 is toggled to the configuration of FIG. 2 .
- hot superheated vapor phase refrigerant discharged from compressor outlet 28 is conveyed to the valve-side port 62 of source heat exchanger 18 via fluid line 34 , valve 14 , and fluid line 66 .
- source heat exchanger 18 now serves as a condenser to extract heat from the hot vapor phase refrigerant, and deposit the extracted heat Q 3 at source S by thermal exchange between the refrigerant and the working fluid circulating through fluid lines 64 .
- Subcooled liquid exits source heat exchanger 18 at the economizer-side port 60 and passes through filter 26 as described above.
- the subcooled liquid then passes through primary thermal expansion valve 22 , where the refrigerant is expanded to a cold vapor/liquid mixture and discharged to fluid line 50 B.
- fluid line 52 A At fluid divider 51 , no refrigerant flow passes to fluid line 52 A toward economizer expansion valve 24 , but rather, the entire volume of refrigerant passes from line 50 B to line 50 A and on to economizer 20 .
- no fluid circulates from crossflow inlet 48 A to crossflow outlet 46 A of economizer 20 , and therefore no substantial heat transfer occurs within economizer heat exchanger 20 .
- the cold vapor/fluid mixture which enters economizer 20 at the source-side port 48 exits the load-side port 46 with substantially unchanged temperature, pressure and phase.
- economizer expansion valve 24 may be adjusted to a fully closed position. This prevents fluid flow therethrough, such that no fluid passage through fluid lines 52 A, 52 B and 54 B occurs.
- valve 24 is an electronic expansion valve (EEV) which can be continuously adjusted between fully closed and fully opened positions, as well as any selected intermediate position.
- EEV electronic expansion valve
- controller 70 may automatically adjust valve 24 to a fully closed, zero-flow position when air conditioning system 10 is toggled from the heating mode to the cooling mode.
- economizer expansion valve 24 may be a thermostatic expansion valve (TXV) together with a solenoid operable to separately permit or prevent flow therethrough.
- the thermostatic expansion valve may change the size of its fluid flow passageway responsive to pressure and/or temperature changes, while the solenoid operates as an open/closed only valve.
- the lack of fluid flow through economizer expansion valve 24 also results in a lack of flow through vapor injection fluid line 54 B, such that no vapor is injected at vapor injection inlet 32 of compressor 12 . Accordingly, the vapor injection functionality provided in the heating mode of FIG. 1 is operably disabled and the cooling mode of FIG. 2 by the closure of expansion valve 24 .
- the mixed vapor/liquid phase refrigerant discharged at the load-side port 46 of economizer 20 is carried to economizer-side port 40 of load heat exchanger 16 by fluid line 44 , where heat Q 1 is transferred to the cool vapor mixture from building B.
- cooled working fluid circulates from crossflow outlet 38 A, through working fluid lines 42 and into building B, where the working fluid is warmed by the ambient air of building B.
- This warmed working fluid is carried by working fluid lines 42 back to crossflow inlet 40 A of load heat exchanger 16 , where the flow of the relatively colder vapor/liquid refrigerant absorbs heat Q 1 , such that the refrigerant is converted to a superheated vapor phase by the time it is discharged at the compressor-side port 38 .
- Fluid line 36 conveys the superheated vapor through valve 14 to fluid line 68 , and then to compressor inlet 30 , where the low-pressure superheated vapor is again compressed for a new refrigerant cycle.
- compressor 12 operates with relatively high compression ratios in the heating mode of FIG. 1 , in order to provide the requisite heat for conditioning building B by deposit of heat Q 1 therein.
- a vapor compression functionality as shown in FIG. 1 and described in detail above provides substantial increases in capacity and efficiency of air conditioning system 10 .
- compressor 12 may utilize lower compression ratios between inlet 30 and outlet 28 while still providing adequate removal of heat Q 1 from building B.
- vapor injection is unnecessary and that functionality may therefore be disabled without an efficiency penalty.
- the operable disabling of vapor injection may be accomplished entirely by controller 70 e.g., by issuing a command for economizer expansion valve 24 to fully close when reversing valve 14 to toggle from the heating to the cooling mode.
- compressor 12 is a variable speed scroll-type compressor.
- Scroll compressors also known as spiral compressors, use two interleaving scrolls to pump fluid from an inlet to an outlet, such as by fixing one scroll while the other orbits eccentrically without rotating, thereby trapping and pumping or compressing pockets of fluid between the scrolls.
- the superheated vapor received at the vapor injection port may be injected to the scroll set at an intermediate point of the compression process. The size and position of these ports can be optimized to ensure maximum benefit and coefficient of performance and capacity for scroll compressor 12 at expected operating conditions for a particular application.
- compressor 12 includes vapor injection inlet 32 on an outer surface of compressor shell 126 , leading to a vapor transfer tube 120 extending into the interior of compressor 12 around scroll 122 to manifold 138 .
- Manifold 138 delivers the vapor to vapor injection outlets 124 via lateral passageway 140 formed in stationary scroll 136 .
- Outlets 124 may be positioned along passageway 140 at any selected location to correspond with a selected wrap of scroll 122 .
- Outlets 124 deliver vapor V within working pockets defined between the scroll wraps which are at an intermediate pressure between the low pressure at inlet 32 ( FIG. 1 ) and the high pressure at outlet 28 ( FIG. 1 ).
- superheated vapor flowing from economizer 20 is received at vapor injection inlet 32 , and is then delivered via tube 120 and outlets 124 to a desired location among the wraps of scroll 122 .
- the particular location of outlets 124 among the wraps of scroll 122 can be selected for a particular application, in order to provide superheated vapor to scroll 122 at a desired location for maximum efficiency of compressor 12 .
- Variable speeds used in compressor 12 further allows precise matching of compressor output to the load demanded for a particular application.
- scroll 136 is a fixed scroll while moveable scroll 122 may orbited relative to scroll 136 at a variable speed to provide the variable speed function of compressor 12 .
- the variable loads imposed by heating and cooling cycles may be met by varying the speed of compressor 12 .
- the variable-speed operation facilitates a steady ramp up and ramp down as compressor 12 changes speed, such that a refrigerant buffer tank may be kept to a minimal size.
- economizer 20 is a coaxial heat exchanger 80 , shown in FIG. 4 .
- Coaxial heat exchanger 80 includes outer fluid passageway 82 with a coaxial inner fluid passageway 84 received therewithin, as shown in FIG. 5 .
- the coaxial arrangement of passageways 82 and 84 may form a plurality of coils 86 ( FIG. 4 ) to provide a desired axial extent of passageways 82 , 84 while consuming a minimal amount of physical space.
- Outer passageway 82 includes axial ends 88 which sealingly engage the outer surface of the adjacent inner passageway 84 , and include inlet 90 and outlet 92 radially spaced from the outer surface of the main axially extending body of outer passageway 82 .
- An incoming flow F 1 is received at inlet 90 , as best seen in FIG. 5 , and proceeds to flow around the outer surface of inner fluid passageway 84 until reaching outlet 92 where it is discharged as outlet flow F 2 .
- an inlet flow F 3 flows into inner fluid passageway 84 at inlet 96 , and flows along the opposite axial direction through inner passageway 84 to be discharged at outlet 94 as flow F 4 , while remaining fluidly isolated from the flow through outer passageway 82 .
- This “counter-flow” arrangement in which the inlet 90 of outer fluid passageway 82 is adjacent the outlet 94 of the inner fluid passageway 84 and vice-versa, promotes maximum heat transfer between the respective working fluids by maximizing the temperature differential throughout the axial extent of coaxial heat exchanger 80 .
- one of the fluid flows may be reversed so that both working fluids travel along the same direction.
- inner fluid passageway 84 may include a plurality of corrugations 98 arranged in a helical threadform-type pattern, which encourages the development of a twisting, turbulent flow through both outer and inner fluid passageways 82 , 84 . This flow ensures that the working fluids in passageways 82 , 84 remain well mixed to promote thorough heat transfer between the two fluids throughout the axial extent of heat exchanger 80 .
- coaxial heat exchanger 80 for economizer 20 in air conditioning system 10 helps to ensure delivery of sub-cooled liquid to expansion valve 22 , while also ensuring that the vapor injection flow through fluid line 54 B to vapor injection port 32 ( FIG. 1 ) is always superheated.
- the coaxial heat exchanger arrangement shown in FIGS. 4 and 5 provides a large amount of heat transfer between the fluid flows, thereby promoting the provision of pure superheated vapor to the vapor injection port 32 of compressor 12 , which may be designed to handle only vapor such as in the case of scroll compressor 12 described above.
- the heat transfer enabled by economizer 20 also ensures that only subcooled liquid is provided to expansion valve 22 , which may operate properly and efficiently (e.g., without “hunting” or erratic adjustment behavior) when pure liquid is delivered.
- heat exchanger 80 may be designed to operate using potable water in one or both of passageways 82 , 84 .
- coaxial heat exchanger 80 may also be used for load heat exchanger 16 , in which the working fluid circulating through working fluid lines 42 to building B may be water designed to be delivered to the end user, such as hot water for a hot water heater which discharges to building appliances.
- source heat exchanger 18 may be a coaxial heat exchanger 80 , designed for either potable or non-potable fluid flows.
- economizer 20 may be formed as flash tank 100 , shown in FIG. 6 .
- a flow F 5 of refrigerant is received at inlet 102 in a mixed phase, such as a partially subcooled refrigerant of the type carried by fluid line 44 shown in FIG. 1 .
- This refrigerant is allowed to expand or “flash” into vapor upon entry into flash tank 100 .
- Saturated vapor 104 rises toward outlet 106 , passing through a de-entrainment mesh pad 108 to remove any entrained liquid in vapor 104 .
- This drier, but still saturated vapor 110 flows from outlet 106 to the vapor injection port of a compressor, such as inlet 32 of compressor 12 via fluid line 54 B as shown in FIG.
- residual liquid 112 collects at the bottom of flash tank 100 , the level of which is measured by fluid level measuring device 114 .
- a control valve 116 connected at liquid outlet 118 may be opened (to lower the level) or closed (to allow further liquid accumulation).
- the sub-cooled liquid 112 may be discharged to an expansion valve, such as expansion valve 22 via fluid lines 50 A, 50 B.
- the provision of saturated vapor 110 to a vapor injection port of a compressor is not optimal, because in some cases such vapor may include droplets of liquid refrigerant, for which the compressor, such as scroll compressor 12 , is not designed.
- the level of liquid 112 within flash tank 100 must be controlled within a given range, and is influenced by the particular refrigerant properties received at flow F 5 , as well as the volume of flow.
- flash tank 100 must be sized according to other system parameters of air conditioning system 10 in order to work properly, and the working parameters of system 10 may only be changed within a certain range without overwhelming the capacities of flash tank 100 .
- the exemplary embodiment of air conditioning system 10 shown in FIGS. 1 and 2 utilizes coaxial heat exchanger 80 for economizer 20 , rather than flash tank 100 .
- the refrigerant flow used for the thermal cycle of air conditioning system 10 is R410A refrigerant.
- R410A may be used in a transcritical cycle, i.e., the refrigerant may be present in both sub-critical and super-critical states at different points along its fluid path.
- a super-critical fluid is a fluid having a temperature and pressure above its critical point, at which distinct liquid and gas phases do not exist.
- the “vapor/liquid mixture” referred to above with respect to the heating and cooling cycles shown in FIGS. 1 and 2 may be super-critical fluids.
- Sub-critical fluids are fluids in which distinct liquid and gas phases do exist, such as subcooled liquid and superheated vapor as described in detail above with respect to the heating and cooling cycles of FIGS. 1 and 2 respectively.
- R410A refrigerant can traverse sub-critical and super-critical states without itself changing phase, such that a higher temperature refrigerant may be utilized for more effective heat transfer at various stages of air conditioning system 10 .
- R410A is also widely used in homes and buildings for primary heating/cooling needs in the United States as well as elsewhere in the world, and is readily commercially available in sufficient quantity for small- or large-scale heating/cooling needs for a reasonable price.
- R410A is also generally accepted under local, state, and federal codes.
- refrigerant candidates may include R134a, R32, R1234ze, or blends of any of the previously mentioned refrigerants.
- controller 70 is electrically connected to compressor 12 , 4-way reversing valve 14 , economizer expansion valve 24 and primary expansion valve 22 , as shown in FIGS. 1 and 2 .
- controller 70 toggles 4-way reversing valve 14 into the illustrated configuration, opens economizer expansion valve 24 to an appropriate fluid flow capacity, and adjusts primary expansion valve 22 to produce a desired vapor mixture carried by fluid lines 56 A, 56 B from the expected sub-cooled liquid arriving from fluid line 50 B.
- Controller 70 activates compressor 12 , which sets the heating cycle in motion by compelling refrigerant to pass through the various functional structures of air conditioning system 10 to effect heating in building B, as described in detail above.
- controller 70 receives signals indicative of fluid pressures within expansion valves 22 , 24 , as measured by pressure sensing lines 58 , 54 A, respectively.
- Controller 70 includes a comparator which compares the pressures within pressure sensing lines 58 , 54 A of valves 22 , 24 , respectively, against a desired pressure for a particular application. This comparison results in a disparity between the desired and actual pressure, which is then compared against a threshold acceptable disparity. When the actual disparity is beyond the threshold disparity, controller 70 adjusts the fluid flow through valves 22 , 24 and/or the speed of compressor 12 in order to bring the pressure within pressure sensing lines 58 , 54 A to a level within the desired disparity.
- controller 70 toggles 4-way reversing valve 14 from the configuration of FIG. 1 to the configuration of FIG. 2 .
- controller 70 adjusts economizer expansion valve 24 to a fully closed position, thereby operably disabling the vapor injection feature used in the heating mode, as described in detail above.
- Primary expansion valve 22 may also be adjusted to the differing demands of receiving sub-cooled liquid from fluid line 56 A and discharging a vapor mixture to fluid lines 50 B, as described above.
- Controller 70 may then activate compressor 12 in order to compel the refrigerant throughout the refrigerant circuit shown in FIG. 2 and effect cooling of building B as described above.
- controller 70 may adjust the speed of compressor 12 and/or the flow characteristics through valve 22 in order to maintain the pressure within pressure sensing line 58 in an acceptable range.
- the desired pressure within valve 22 and line 58 is lower in the cooling mode of air conditioning system 10 as compared to the heating mode thereof. Therefore, compressor 12 is generally controlled by controller 70 to operate at a slower and/or lower power state in the cooling mode as compared to the heating mode.
- the present system may be used in the following particularized applications.
- air conditioning system 10 may be used in a geothermal system, in which source heat exchanger 18 is in heat exchange relationship with a ground source/loop 64 as a heat source/heat sink S.
- Air conditioning system 10 may also be used for hot water heating for hydronic applications, such as residential or business heating systems which use water as a heat-transfer medium for heating the air inside a building. Such systems include radiant-heat applications, for example.
- working fluid lines 42 may carry hot water to building B, deposit heat Q 1 therein, and recirculate to load heat exchanger 16 to be reheated.
- Air conditioning system 10 utilized with forced-air type air conditioning is illustrated in FIG. 7 .
- Air conditioning system 10 is contained within a single housing 128 , as shown, which also includes air movers (not shown) for inducing air flow F through ducts 42 (in the forced-air context of FIG. 7 , ducts are the working fluid conduits 42 of FIG. 1 and air is the working fluid).
- Source S is a ground source, such as an underground formation of soil, rock, water, and the like.
- heat Q 3 is deposited into the underground formation by warm working fluid circulating through fluid lines 64 , and withdrawn from building B as heat Q 1 via ducts 42 .
- heat Q 3 is withdrawn from the underground formation by cool working fluid circulating through fluid lines 64 , and deposited into building B as heat Q 1 via ducts 42 .
- air conditioning system 10 may also be used for domestic or commercial hot water heating.
- Such systems convey hot working fluid from air conditioning system 10 (e.g., from load heat exchanger 16 ) through hot water line 132 to a water heater 130 which may be located, e.g., in building B.
- Cool water is returned to air conditioning system 10 (e.g., back to load heat exchanger 16 ) via a cool water line 134 to be reheated.
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Abstract
An air conditioning system can be toggled between a heating mode, in which heat is withdrawn from a source (e.g., a geothermal source) and deposited into a conditioned space (e.g., a building), and a cooling mode, in which heat is withdrawn from the conditioned space and deposited into the source. The air conditioning system uses a combination of efficiency-enhancing technologies, including injection of superheated vapor into the system's compressor from an economizer circuit, adjustable compressor speed, the use of one or coaxial heat exchangers and the use of electronic expansion valves that are continuously adjustable from a fully closed to various open positions. A controller may be used to control the system for optimal performance in both the heating and cooling modes, such as by disabling the economizer circuit and vapor injection when the system is in the cooling mode.
Description
This application claims the benefit of and priority to U.S. Provisional Patent Application No. 62/056,082 filed on Sep. 26, 2014 entitled AIR CONDITIONING SYSTEM WITH VAPOR INJECTION COMPRESSOR, which is incorporated by reference herein in its entirety.
1. Technical Field
The present disclosure relates to air conditioning systems and, in particular, to efficient-enhanced reversible air conditioning systems capable of both heating and refrigeration.
2. Description of the Related Art
Heating and cooling systems may include a compressor for compressing a working refrigerant fluid, a condenser heat exchanger for extracting heat from the refrigerant fluid, an expansion valve, and an evaporator heat exchanger for extracting heat from an external source. In some instances, such refrigeration systems may further include an economizer heat exchanger and/or a vapor injection feature associated with the compressor for increasing both the capacity and the efficiency of the compressor.
In typical refrigeration systems, the refrigerant is a high pressure hot liquid upon leaving the compressor, is a high pressure warm liquid downstream of the condenser, is a low pressure warm gas downstream of the expansion valve, and is a low pressure cool gas downstream of the evaporator.
An economizer may be used to further influence the thermal state of the refrigerant between the condenser and evaporator. An auxiliary refrigerant flow is tapped from the main refrigerant flow downstream of the economizer heat exchanger and passed through an expansion valve to expand the auxiliary refrigerant flow before same is passed back through the economizer heat exchanger in heat exchange relation with the main refrigerant flow. This serves to further subcool the main refrigerant flow upstream of the evaporator.
The economizer heat exchanger also discharges an auxiliary refrigerant flow in the form of an intermediate pressure vapor, which is then injected into the compressor. Typically a scroll compressor is used in connection with such a system, and the vapor is injected at an intermediate pressure location within the wraps of the scroll compressor.
Further increases in efficiency and capacity are desirable in air conditioning systems, in order to increase system efficacy and/or decrease the cost of operating the system.
The present disclosure provides an air conditioning system which can be toggled between a heating mode, in which heat is withdrawn from a source (e.g., a geothermal source) and deposited into a conditioned space (e.g., a building), and a cooling mode, in which heat is withdrawn from the conditioned space and deposited into the source. The air conditioning system uses a combination of efficiency-enhancing technologies, including injection of superheated vapor into the system's compressor from an economizer circuit, adjustable compressor speed, the use of one or more coaxial heat exchangers and the use of electronic expansion valves that are continuously adjustable from a fully closed to various open positions. A controller may be used to control the system for optimal performance in both the heating and cooling modes, such as by disabling the economizer circuit and vapor injection when the system is in the cooling mode.
The above mentioned and other features and objects of this invention, and the manner of attaining them, will become more apparent and the invention itself will be better understood by reference to the following description of embodiments of the invention taken in conjunction with the accompanying drawings, wherein:
Corresponding reference characters indicate corresponding parts throughout the several views. Although the exemplifications set out herein illustrate embodiments of the invention, the embodiments disclosed below are not intended to be exhaustive or to be construed as limiting the scope of the invention to the precise form disclosed.
For purposes of the present disclosure, “air conditioning” refers to both heating and cooling a conditioned space (e.g., the inside of a building). In particular and as described in detail below, an air conditioning system may be reversible to cool a conditioned space while exhausting heat to a source (e.g., a geothermal source), or to heat a conditioned space by extracting heat from the source.
For purposes of the present disclosure, “superheated vapor” refers to a vapor whose temperature is measurably above its liquid/vapor phase change temperature for a given vapor pressure.
For purposes of the present disclosure, “subcooled liquid” refers to a liquid whose temperature is measurably below its liquid/vapor phase change temperature for a given ambient vapor pressure.
For purposes of the present disclosure, “vapor mixture” refers to mixed liquid-and-vapor phase fluid in which the fluid can undergo phase changes (i.e., from liquid to saturated vapor or from saturated vapor to liquid) at constant pressure and temperature.
Referring generally to FIGS. 1 and 2 , the present disclosure provides air conditioning system 10 which is reconfigurable between a heating mode (FIG. 1 ) and a cooling mode (FIG. 2 ). Such reconfiguration may be accomplished by actuation of a four way reversing valve 14, which reverses the direction of refrigerant flow among the various components of system 10, thereby reversing the flow of heat to and from a source S (e.g., a geothermal source) and a load B (e.g., the interior of a building or other thermally conditioned space). System 10 may further include an economizer heat exchanger 20 which enables a vapor injection feature to enhance the efficiency and function of the compressor 12 in the heating mode, but may not be needed in the cooling mode. As described in detail below, the toggling of reversing valve 14 from the heating mode to the cooling mode may be accompanied by adjusting an economizer expansion valve 24 to cease refrigerant flow therethrough, effectively disabling the vapor injection in the cooling mode.
Regardless of whether air conditioning system 10 is utilized for heating or cooling a conditioned space, the same set of components all remain disposed in the system flow path, the specific functions of which are discussed in detail below. System 10 includes compressor 12 fluidly connected to load heat exchanger 16 and source heat exchanger 18 via reversing valve 14. Operably interposed between load heat exchanger 16 and source heat exchanger 18 is economizer heat exchanger 20. Primary expansion valve 22 is operably interposed between economizer 20 and source heat exchanger 18, while economizer expansion valve 24 selectively receives a portion of the refrigerant flow and discharges to economizer 20 in the heating mode. In the cooling mode of FIG. 2 , economizer expansion valve 24 prevents one of the two flows of refrigerant through economizer heat exchanger 20, effectively nullifying the effect of economizer 20 on the thermal characteristics of air conditioning system 10, as also described in detail below.
1. Reversible Heating and Cooling
The removal of heat Q1 from the refrigerant as it passes through load heat exchanger 16 effects a phase change from superheated vapor (at the compressor-side port 38) to a partially subcooled liquid (at economizer-side port 40), which is discharged to fluid line 44 and conveyed to the load-side port 46 of economizer heat exchanger 20. The refrigerant flows through heat exchanger 20, which removes heat Q2 therefrom as described below. Upon discharge from economizer heat exchanger 20 at the source-side port 48, the full volume of refrigerant flow passes through fluid line 50A to fluid divider 51, where a main flow of refrigerant continues toward source heat exchanger 18 via fluid line 50B, while a portion of the refrigerant is diverted into fluid line 52A and flows toward economizer expansion valve 24.
At expansion valve 24, subcooled liquid refrigerant is allowed to expand into a low-pressure, cool liquid- and vapor mixed-phase state. Pressure sensing line 54A is fluidly connected to expansion valve 24, such that the pressure within valve 24 can be monitored remotely, e.g., by controller 70 (further described below). The low-pressure, mixed-phase refrigerant discharged from valve 24 is transmitted through fluid line 52B to a crossflow inlet 48A of economizer 20 where it circulates in heat-transfer relationship with the main refrigerant flow until reaching crossflow outlet 46A. During this circulation, heat Q2 transfers from the warmer main flow of liquid refrigerant passing from port 46 to port 48 to the low-pressure flow of the economizer portion of refrigerant, such that the refrigerant is warmed to a low-pressure superheated vapor by the time it discharges at outlet 46A. This superheated vapor is carried by vapor injection fluid line 54B to vapor injection inlet 32 of compressor 12.
The transfer of heat Q2 also serves to further lower the temperature of the subcooled liquid phase refrigerant exiting the source-side port 48, as compared to the liquid phase refrigerant entering at the load-side port 46. As noted above, a main flow of this lower-temperature subcooled liquid phase refrigerant passes divider 51 and flows through fluid line 50B to primary expansion valve 22. In valve 22, the sub-cooled liquid is allowed to expand into a low-pressure, cold, mixed liquid/vapor phase. This cold fluid is conveyed via fluid line 56A to a filter/dryer 26, which separates entrained liquid from the vapor and discharges the cold liquid and vapor to fluid line 56B, which conveys the refrigerant to the economizer-side port 60 of source heat exchanger 18.
The cold mixed-phase refrigerant received at economizer-side port 60 passes through source heat exchanger 18, receiving heat Q3 from working fluid circulating through source heat exchanger 18 from source S, thereby warming up to a low-pressure, superheated vapor phase refrigerant which is discharged at the valve-side port 62. Source S may be, for example, a geothermal source which is at a consistently warmer temperature than the cold refrigerant received at the economizer-side port 60. Cooled working fluid is circulated from crossflow outlet 60A, through working fluid lines 64 circulating through source S where the working fluid is warmed, and back to source heat exchanger 18 at crossflow inlet 62A. The warmed working fluid is then ready to discharge heat Q3 to the cold refrigerant as noted above.
In an exemplary embodiment, the working fluid circulating through load heat exchanger 16 may be, e.g., water, while the working fluid circulating through source heat exchanger 18 may be, e.g., water, methanol, propylene glycol, or ethylene glycol.
The low-pressure, superheated vapor discharged from the valve-side port 62 of source heat exchanger 18 is conveyed via fluid line 66 to reversing valve 14, where it is allowed to pass to fluid line 68, which in turn conveys the vapor to compressor inlet 30 to be compressed for the next refrigerant cycle.
Turning now to FIG. 2 , a cooling mode of air conditioning system 10 is illustrated in which refrigerant flow is substantially reversed from the heating mode of FIG. 1 , and the discharge of heated vapor from economizer 20 to compressor 12 is ceased such that vapor injection functionality is operably disabled.
To reverse the refrigerant flow direction from heating to cooling mode, 4-way reversing valve 14 is toggled to the configuration of FIG. 2 . Thus, as illustrated, hot superheated vapor phase refrigerant discharged from compressor outlet 28 is conveyed to the valve-side port 62 of source heat exchanger 18 via fluid line 34, valve 14, and fluid line 66. Rather than transferring heat to the conditioned space of building B via load heat exchanger 16 as shown in FIG. 1 and described in detail above, source heat exchanger 18 now serves as a condenser to extract heat from the hot vapor phase refrigerant, and deposit the extracted heat Q3 at source S by thermal exchange between the refrigerant and the working fluid circulating through fluid lines 64.
Subcooled liquid exits source heat exchanger 18 at the economizer-side port 60 and passes through filter 26 as described above. The subcooled liquid then passes through primary thermal expansion valve 22, where the refrigerant is expanded to a cold vapor/liquid mixture and discharged to fluid line 50B. At fluid divider 51, no refrigerant flow passes to fluid line 52A toward economizer expansion valve 24, but rather, the entire volume of refrigerant passes from line 50B to line 50A and on to economizer 20. Thus, no fluid circulates from crossflow inlet 48A to crossflow outlet 46A of economizer 20, and therefore no substantial heat transfer occurs within economizer heat exchanger 20. Thus, the cold vapor/fluid mixture which enters economizer 20 at the source-side port 48 exits the load-side port 46 with substantially unchanged temperature, pressure and phase.
In order to stop the diversion of refrigerant flow at divider 51 and therefore effectively disable economizer 20, economizer expansion valve 24 may be adjusted to a fully closed position. This prevents fluid flow therethrough, such that no fluid passage through fluid lines 52A, 52B and 54B occurs. In an exemplary embodiment, valve 24 is an electronic expansion valve (EEV) which can be continuously adjusted between fully closed and fully opened positions, as well as any selected intermediate position. Advantageously, the use of an EEV for economizer expansion valve 24 allows controller 70 to control valve 24 automatically according to a programmed set of instructions. As described in detail below, controller 70 may automatically adjust valve 24 to a fully closed, zero-flow position when air conditioning system 10 is toggled from the heating mode to the cooling mode. However, it is contemplated that economizer expansion valve 24 may be a thermostatic expansion valve (TXV) together with a solenoid operable to separately permit or prevent flow therethrough. The thermostatic expansion valve may change the size of its fluid flow passageway responsive to pressure and/or temperature changes, while the solenoid operates as an open/closed only valve.
Referring still to FIG. 2 , the lack of fluid flow through economizer expansion valve 24 also results in a lack of flow through vapor injection fluid line 54B, such that no vapor is injected at vapor injection inlet 32 of compressor 12. Accordingly, the vapor injection functionality provided in the heating mode of FIG. 1 is operably disabled and the cooling mode of FIG. 2 by the closure of expansion valve 24.
The mixed vapor/liquid phase refrigerant discharged at the load-side port 46 of economizer 20 is carried to economizer-side port 40 of load heat exchanger 16 by fluid line 44, where heat Q1 is transferred to the cool vapor mixture from building B. In particular, cooled working fluid circulates from crossflow outlet 38A, through working fluid lines 42 and into building B, where the working fluid is warmed by the ambient air of building B. This warmed working fluid is carried by working fluid lines 42 back to crossflow inlet 40A of load heat exchanger 16, where the flow of the relatively colder vapor/liquid refrigerant absorbs heat Q1, such that the refrigerant is converted to a superheated vapor phase by the time it is discharged at the compressor-side port 38. Fluid line 36 conveys the superheated vapor through valve 14 to fluid line 68, and then to compressor inlet 30, where the low-pressure superheated vapor is again compressed for a new refrigerant cycle.
Advantageously, the disabling of the vapor injection functionality in the cooling mode, while enabling the same in the heating mode, allows efficiency gains to be realized in a reversible heat pump system. In particular, compressor 12 operates with relatively high compression ratios in the heating mode of FIG. 1 , in order to provide the requisite heat for conditioning building B by deposit of heat Q1 therein. Thus, in view of the larger work load borne by compressor 12 during the heating mode, a vapor compression functionality as shown in FIG. 1 and described in detail above provides substantial increases in capacity and efficiency of air conditioning system 10. However, in the cooling mode of FIG. 2 , compressor 12 may utilize lower compression ratios between inlet 30 and outlet 28 while still providing adequate removal of heat Q1 from building B. At these lower compression ratios, vapor injection is unnecessary and that functionality may therefore be disabled without an efficiency penalty. Advantageously, the operable disabling of vapor injection may be accomplished entirely by controller 70 e.g., by issuing a command for economizer expansion valve 24 to fully close when reversing valve 14 to toggle from the heating to the cooling mode.
2. Variable-Speed Scroll Compressor
In an exemplary embodiment, compressor 12 is a variable speed scroll-type compressor. Scroll compressors, also known as spiral compressors, use two interleaving scrolls to pump fluid from an inlet to an outlet, such as by fixing one scroll while the other orbits eccentrically without rotating, thereby trapping and pumping or compressing pockets of fluid between the scrolls. Advantageously, the superheated vapor received at the vapor injection port may be injected to the scroll set at an intermediate point of the compression process. The size and position of these ports can be optimized to ensure maximum benefit and coefficient of performance and capacity for scroll compressor 12 at expected operating conditions for a particular application.
In one exemplary embodiment shown in FIG. 3 , compressor 12 includes vapor injection inlet 32 on an outer surface of compressor shell 126, leading to a vapor transfer tube 120 extending into the interior of compressor 12 around scroll 122 to manifold 138. Manifold 138 delivers the vapor to vapor injection outlets 124 via lateral passageway 140 formed in stationary scroll 136. Outlets 124 may be positioned along passageway 140 at any selected location to correspond with a selected wrap of scroll 122. Outlets 124 deliver vapor V within working pockets defined between the scroll wraps which are at an intermediate pressure between the low pressure at inlet 32 (FIG. 1 ) and the high pressure at outlet 28 (FIG. 1 ). Thus, superheated vapor flowing from economizer 20 is received at vapor injection inlet 32, and is then delivered via tube 120 and outlets 124 to a desired location among the wraps of scroll 122. Advantageously, the particular location of outlets 124 among the wraps of scroll 122 can be selected for a particular application, in order to provide superheated vapor to scroll 122 at a desired location for maximum efficiency of compressor 12.
Variable speeds used in compressor 12 further allows precise matching of compressor output to the load demanded for a particular application. In the embodiment of FIG. 3 , scroll 136 is a fixed scroll while moveable scroll 122 may orbited relative to scroll 136 at a variable speed to provide the variable speed function of compressor 12. In the illustrated reversible embodiment of FIGS. 1 and 2 , the variable loads imposed by heating and cooling cycles (as noted above) may be met by varying the speed of compressor 12. Further, the variable-speed operation facilitates a steady ramp up and ramp down as compressor 12 changes speed, such that a refrigerant buffer tank may be kept to a minimal size.
3. Coaxial Heat Exchangers
In an exemplary embodiment, economizer 20 is a coaxial heat exchanger 80, shown in FIG. 4 . Coaxial heat exchanger 80 includes outer fluid passageway 82 with a coaxial inner fluid passageway 84 received therewithin, as shown in FIG. 5 . The coaxial arrangement of passageways 82 and 84 may form a plurality of coils 86 (FIG. 4 ) to provide a desired axial extent of passageways 82, 84 while consuming a minimal amount of physical space. Outer passageway 82 includes axial ends 88 which sealingly engage the outer surface of the adjacent inner passageway 84, and include inlet 90 and outlet 92 radially spaced from the outer surface of the main axially extending body of outer passageway 82.
An incoming flow F1 is received at inlet 90, as best seen in FIG. 5 , and proceeds to flow around the outer surface of inner fluid passageway 84 until reaching outlet 92 where it is discharged as outlet flow F2. Similarly, an inlet flow F3 flows into inner fluid passageway 84 at inlet 96, and flows along the opposite axial direction through inner passageway 84 to be discharged at outlet 94 as flow F4, while remaining fluidly isolated from the flow through outer passageway 82. This “counter-flow” arrangement, in which the inlet 90 of outer fluid passageway 82 is adjacent the outlet 94 of the inner fluid passageway 84 and vice-versa, promotes maximum heat transfer between the respective working fluids by maximizing the temperature differential throughout the axial extent of coaxial heat exchanger 80. However, in some instances, one of the fluid flows may be reversed so that both working fluids travel along the same direction.
In the exemplary embodiment of FIG. 5 , inner fluid passageway 84 may include a plurality of corrugations 98 arranged in a helical threadform-type pattern, which encourages the development of a twisting, turbulent flow through both outer and inner fluid passageways 82, 84. This flow ensures that the working fluids in passageways 82, 84 remain well mixed to promote thorough heat transfer between the two fluids throughout the axial extent of heat exchanger 80.
Advantageously, employing coaxial heat exchanger 80 for economizer 20 in air conditioning system 10 helps to ensure delivery of sub-cooled liquid to expansion valve 22, while also ensuring that the vapor injection flow through fluid line 54B to vapor injection port 32 (FIG. 1 ) is always superheated. In particular, the coaxial heat exchanger arrangement shown in FIGS. 4 and 5 provides a large amount of heat transfer between the fluid flows, thereby promoting the provision of pure superheated vapor to the vapor injection port 32 of compressor 12, which may be designed to handle only vapor such as in the case of scroll compressor 12 described above. The heat transfer enabled by economizer 20 also ensures that only subcooled liquid is provided to expansion valve 22, which may operate properly and efficiently (e.g., without “hunting” or erratic adjustment behavior) when pure liquid is delivered.
In a further exemplary embodiment, heat exchanger 80 may be designed to operate using potable water in one or both of passageways 82, 84. For example, coaxial heat exchanger 80 may also be used for load heat exchanger 16, in which the working fluid circulating through working fluid lines 42 to building B may be water designed to be delivered to the end user, such as hot water for a hot water heater which discharges to building appliances. It is also contemplated that source heat exchanger 18 may be a coaxial heat exchanger 80, designed for either potable or non-potable fluid flows.
In some instances, economizer 20 may be formed as flash tank 100, shown in FIG. 6 . In this arrangement, a flow F5 of refrigerant is received at inlet 102 in a mixed phase, such as a partially subcooled refrigerant of the type carried by fluid line 44 shown in FIG. 1 . This refrigerant is allowed to expand or “flash” into vapor upon entry into flash tank 100. Saturated vapor 104 rises toward outlet 106, passing through a de-entrainment mesh pad 108 to remove any entrained liquid in vapor 104. This drier, but still saturated vapor 110 flows from outlet 106 to the vapor injection port of a compressor, such as inlet 32 of compressor 12 via fluid line 54B as shown in FIG. 1 . Meanwhile, residual liquid 112 collects at the bottom of flash tank 100, the level of which is measured by fluid level measuring device 114. Depending on the measured level of liquid 112, a control valve 116 connected at liquid outlet 118 may be opened (to lower the level) or closed (to allow further liquid accumulation). The sub-cooled liquid 112 may be discharged to an expansion valve, such as expansion valve 22 via fluid lines 50A, 50B.
However, the provision of saturated vapor 110 to a vapor injection port of a compressor is not optimal, because in some cases such vapor may include droplets of liquid refrigerant, for which the compressor, such as scroll compressor 12, is not designed. Further, the level of liquid 112 within flash tank 100 must be controlled within a given range, and is influenced by the particular refrigerant properties received at flow F5, as well as the volume of flow. Thus, flash tank 100 must be sized according to other system parameters of air conditioning system 10 in order to work properly, and the working parameters of system 10 may only be changed within a certain range without overwhelming the capacities of flash tank 100. In order to provide flexibility for reversible functionality the exemplary embodiment of air conditioning system 10 shown in FIGS. 1 and 2 utilizes coaxial heat exchanger 80 for economizer 20, rather than flash tank 100.
4. Transcritical Refrigerant
In an exemplary embodiment, the refrigerant flow used for the thermal cycle of air conditioning system 10 is R410A refrigerant. In air conditioning system 10, R410A may be used in a transcritical cycle, i.e., the refrigerant may be present in both sub-critical and super-critical states at different points along its fluid path.
For purposes of the present disclosure, a super-critical fluid is a fluid having a temperature and pressure above its critical point, at which distinct liquid and gas phases do not exist. For example, the “vapor/liquid mixture” referred to above with respect to the heating and cooling cycles shown in FIGS. 1 and 2 may be super-critical fluids. Sub-critical fluids, on the other hand, are fluids in which distinct liquid and gas phases do exist, such as subcooled liquid and superheated vapor as described in detail above with respect to the heating and cooling cycles of FIGS. 1 and 2 respectively.
Advantageously, R410A refrigerant can traverse sub-critical and super-critical states without itself changing phase, such that a higher temperature refrigerant may be utilized for more effective heat transfer at various stages of air conditioning system 10. Moreover, R410A is also widely used in homes and buildings for primary heating/cooling needs in the United States as well as elsewhere in the world, and is readily commercially available in sufficient quantity for small- or large-scale heating/cooling needs for a reasonable price. R410A is also generally accepted under local, state, and federal codes.
In some applications in accordance with the present disclosure, other refrigerant candidates may include R134a, R32, R1234ze, or blends of any of the previously mentioned refrigerants.
5. Control and Operation
In operation, controller 70 is electrically connected to compressor 12, 4-way reversing valve 14, economizer expansion valve 24 and primary expansion valve 22, as shown in FIGS. 1 and 2 . In the heating mode (FIG. 1 ), controller 70 toggles 4-way reversing valve 14 into the illustrated configuration, opens economizer expansion valve 24 to an appropriate fluid flow capacity, and adjusts primary expansion valve 22 to produce a desired vapor mixture carried by fluid lines 56A, 56B from the expected sub-cooled liquid arriving from fluid line 50B.
When it is desired to switch from the heating mode of FIG. 1 to the cooling mode of FIG. 2 , controller 70 toggles 4-way reversing valve 14 from the configuration of FIG. 1 to the configuration of FIG. 2 . In addition, controller 70 adjusts economizer expansion valve 24 to a fully closed position, thereby operably disabling the vapor injection feature used in the heating mode, as described in detail above. Primary expansion valve 22 may also be adjusted to the differing demands of receiving sub-cooled liquid from fluid line 56A and discharging a vapor mixture to fluid lines 50B, as described above.
6. Applications.
The present system may be used in the following particularized applications.
In an exemplary embodiment, air conditioning system 10 may be used in a geothermal system, in which source heat exchanger 18 is in heat exchange relationship with a ground source/loop 64 as a heat source/heat sink S.
For example, an exemplary geothermal application of air conditioning system 10 utilized with forced-air type air conditioning is illustrated in FIG. 7 . Air conditioning system 10 is contained within a single housing 128, as shown, which also includes air movers (not shown) for inducing air flow F through ducts 42 (in the forced-air context of FIG. 7 , ducts are the working fluid conduits 42 of FIG. 1 and air is the working fluid). Source S is a ground source, such as an underground formation of soil, rock, water, and the like. In the cooling mode, heat Q3 is deposited into the underground formation by warm working fluid circulating through fluid lines 64, and withdrawn from building B as heat Q1 via ducts 42. Conversely, in the heating mode, heat Q3 is withdrawn from the underground formation by cool working fluid circulating through fluid lines 64, and deposited into building B as heat Q1 via ducts 42.
As noted above and illustrated in FIG. 7 , air conditioning system 10 may also be used for domestic or commercial hot water heating. Such systems convey hot working fluid from air conditioning system 10 (e.g., from load heat exchanger 16) through hot water line 132 to a water heater 130 which may be located, e.g., in building B. Cool water is returned to air conditioning system 10 (e.g., back to load heat exchanger 16) via a cool water line 134 to be reheated.
While this disclosure has been described as having exemplary designs, the present disclosure can be further modified within the spirit and scope of this disclosure. This application is therefore intended to cover any variations, uses, or adaptations of the disclosure using its general principles. Further, this application is intended to cover such departures from the present disclosure as come within known or customary practice in the art to which this disclosure pertains and which fall within the limits of the appended claims.
Claims (19)
1. A reversible heat pump system housed in a housing for heating and cooling a space, comprising:
a refrigerant circuit through which refrigerant is configured to flow;
a variable speed scroll compressor disposed on the refrigerant circuit, the compressor including a compressor inlet, a compressor outlet, and a vapor infection inlet disposed between the compressor inlet and the compressor outlet;
a liquid-to-liquid coaxial counterflow load heat exchanger disposed on the refrigerant circuit to exchange heat between the refrigerant and either a cooling load or a heating load;
a liquid-to-liquid coaxial counterflow source heat exchanger disposed on the refrigerant circuit to exchange heat between the refrigerant and a source;
a reversing valve disposed on the refrigerant circuit between the compressor and the load and source heat exchangers and selectable to effect a heating mode and a cooling mode, wherein in the heating mode the reversing valve routes the refrigerant from the compressor outlet to the load heat exchanger and routes the refrigerant from the source heat exchanger to the compressor inlet, wherein in the cooling mode the reversing valve routes the refrigerant from the compressor outlet to the source heat exchanger and routes the refrigerant from the load heat exchanger to the compressor inlet;
a diverter disposed on the refrigerant circuit between the load heat exchanger and the source heat exchanger, the diverter configured to selectively divert a portion of the refrigerant to an economizer circuit when the heat pump is in the heating mode and none of the refrigerant when the heat pump is in the cooling mode, wherein the economizer circuit includes
a coaxial counterflow economizer heat exchanger configured to exchange heat between the refrigerant diverted to the economizer circuit and the refrigerant in the refrigerant circuit to create superheated refrigerant vapor for injection into the vapor injection inlet, and
an electronic economizer expansion valve (EEEV) disposed between the diverter and the economizer heat exchanger, the EEEV configured to be continuously adjustable between fully open and fully closed positions to selectively meter and expand the diverted refrigerant when the heat pump is in the heating mode and to selectively cease diversion of the refrigerant to the economizer circuit when the heat pump is in the cooling mode; and
an electronic primary expansion valve (EPEV) disposed on the refrigerant circuit between the diverter and the source heat exchanger to selectively meter the refrigerant discharged from the economizer heat exchanger to the source heat exchanger when the heat pump is in the heating mode and the economizer circuit is active, and to selectively meter the refrigerant discharged from the source heat exchanger to the economizer heat exchanger when the heat pump is in the cooling mode and the economizer circuit is inactive,
wherein in the heating mode, the EPEV receives the refrigerant from the economizer heat exchanger and discharges the refrigerant to the source heat exchanger; and
in the cooling mode, the EPEV receives the refrigerant from the source heat exchanger and discharges the refrigerant to the economizer heat exchanger.
2. The reversible heat pump system of claim 1 , including a controller configured to control the EEEV to meter the diverted refrigerant according to a programmed set of instructions.
3. The reversible heat pump system of claim 2 , wherein the controller is operably connected to the reversing valve and the EEEV, the controller operable to:
toggle the reversing valve into the heating mode and adjustably open the EEEV when the reversible heat pump system is called upon to deposit heat into a conditioned space; and
toggle the reversing valve into the cooling mode and close the EEEV to a fully closed position when the reversible heat pump system is called upon to withdraw heat from the conditioned space.
4. The reversible heat pump system of claim 1 , wherein the coaxial counterflow economizer heat exchanger comprises
a first flow path through which the refrigerant in the refrigerant circuit passes; and
a second flow path through which the refrigerant diverted to the economizer circuit passes, the second flow path coaxial with, but fluidly isolated from, the first flow path such that the first flow path is in heat exchange relationship with the second flow path.
5. The reversible heat pump system of claim 1 , wherein at least one of the load heat exchanger and the source heat exchanger comprises
a first flow path through which the refrigerant passes; and
a second flow path through which a first or second working fluid passes, respectively, the second flow path coaxial with, but fluidly isolated from, the first flow path such that the first flow path is in heat exchange relationship with the second flow path.
6. The reversible heat pump system of claim 1 , further comprising a refrigerant filter/dryer disposed on the refrigerant circuit between the source heat exchanger and the EPEV.
7. The reversible heat pump system of claim 1 , further comprising
a compressor inlet pressure sensor configured to detect refrigerant pressure at the compressor inlet; and
a controller operably connected to the compressor, the EPEV, and the compressor inlet pressure sensor, wherein the controller is operable to
compare a compressor inlet pressure indicated by the compressor inlet pressure sensor to a desired compressor inlet pressure to compute a primary pressure difference, and
if the primary pressure difference is beyond a threshold amount, adjust at least one of a speed of the compressor and a flow rate of the refrigerant through the EPEV to return the primary pressure difference to an amount less than the threshold amount.
8. The reversible heat pump system of claim 7 , further comprising a vapor injection pressure sensor configured to detect refrigerant pressure at the vapor injection inlet, wherein the controller is operably connected to the EEEV and to the vapor injection pressure sensor and is operable in the heating mode to
compare a vapor injection inlet pressure indicated by the vapor injection pressure sensor to a desired vapor injection inlet pressure to compute an economizer pressure difference, and
if the economizer pressure difference is beyond a threshold amount, adjust at least one of the speed of the compressor and a flow rate of the diverted refrigerant through the EEEV to return the economizer pressure difference to an amount less than the threshold amount.
9. The reversible heat pump system of claim 1 , wherein the refrigerant is R410A and the heat pump system operates the refrigerant in sub-critical and super-critical states.
10. The reversible heat pump system of claim 1 , wherein
the source is a geothermal source, and
a working fluid circulates between the source heat exchanger and the geothermal source to exchange heat between the refrigerant and the geothermal source.
11. A method of controlling a reversible heat pump system housed in a housing, the method comprising:
toggling a reversing valve into one of a heating mode or a cooling mode, the reversing valve being disposed on a refrigerant circuit between a variable speed scroll compressor disposed on the refrigerant circuit, a liquid-to-liquid coaxial counterflow load heat exchanger disposed on the refrigerant circuit to exchange heat between a refrigerant and either a heating load or a cooling mode, and a liquid-to-liquid coaxial counterflow source heat exchanger disposed on the refrigerant circuit in a heat exchanging arrangement with a source, wherein
in the heating mode, the reversing valve
routes the refrigerant from a compressor outlet of the compressor to the load heat exchanger and
routes refrigerant from the source heat exchanger to a compressor inlet of the compressor, and
in the cooling mode, the reversing valve
routes the refrigerant from the compressor outlet to the source heat exchanger and
routes the refrigerant from the load heat exchanger to the compressor inlet;
controlling an electronic economizer expansion valve (EEEV) configured to be continuously adjustable between fully open and fully closed positions to selectively divert a portion of refrigerant from the refrigerant circuit to a coaxial counterflow economizer heat exchanger, the EEEV being disposed on an economizer circuit between a diverter and the coaxial counterflow economizer heat exchanger, the diverter being disposed on the refrigerant circuit, the coaxial counterflow economizer heat exchanger being configured to exchange heat between the refrigerant diverted to the economizer circuit and the refrigerant in the refrigerant circuit to create superheated refrigerant vapor for injection into a vapor injection inlet of the compressor, including
in the heating mode, adjusting the EEEV to meter and expand the diverted refrigerant and
in the cooling mode, fully closing the EEEV to cease diversion of the refrigerant; and
controlling a speed of the compressor to circulate the refrigerant through the load heat exchanger, the economizer heat exchanger, the source heat exchanger, and an electronic primary expansion valve (EPEV) disposed on the refrigerant circuit between the diverter and the source heat exchanger to match compressor output to a heating load and a cooling load, including
in the heating mode, metering the refrigerant discharged from an active economizer heat exchanger to the source heat exchanger by the EPEV, and
in the cooling mode, metering the refrigerant discharged from the source heat exchanger to an inactive economizer heat exchanger by the EPEV.
12. The method of claim 11 , wherein toggling the reversing valve, controlling the EEEV, and controlling the speed of the compressor are performed by an electronic controller for the heating mode and for the cooling mode.
13. The method of claim 12 , wherein, in the heating mode:
the controller compares a pressure of a vapor injection line with a desired economizer pressure to generate a pressure differential;
the controller compares the pressure differential with a predetermined threshold pressure differential; and
the controller adjusts at least one of the speed of the compressor and a flow rate of the diverted refrigerant when the pressure differential is outside the predetermined threshold pressure differential.
14. The method of claim 12 , wherein in the heating mode and in the cooling mode the controller
compares a pressure in the refrigerant circuit between the reversing valve and the compressor inlet with a desired compressor inlet pressure to generate a pressure differential;
the controller compares the pressure differential with a predetermined threshold pressure differential; and
the controller adjusts at least one of the speed of the compressor and a flow rate of the refrigerant through the EPEV when the pressure differential is outside the predetermined threshold pressure differential.
15. The method of claim 12 , wherein, in the heating mode, the controller controls at least one of the speed of the compressor, a flow rate of the refrigerant through the EPEV, and a flow rate of the diverted refrigerant through the EEEV to maintain the refrigerant in a mixed liquid-and-vapor phase state between the EEEV and the economizer heat exchanger and between the EPEV and the source heat exchanger.
16. The method of claim 12 , wherein, in the cooling mode, the controller controls at least one of the speed of the compressor and a flow rate of the refrigerant through the EPEV to maintain the refrigerant in a mixed liquid-and-vapor phase state between the EPEV and the load heat exchanger.
17. The method of claim 12 , wherein, in the heating mode, the controller controls at least one of the speed of the compressor, a flow rate of the refrigerant through the EPEV, and a flow rate of the refrigerant through the EEEV to maintain the refrigerant in a superheated vapor phase between the load heat exchanger and the compressor, and to maintain the refrigerant in a subcooled liquid phase between the economizer heat exchanger and the EPEV.
18. The reversible heat pump system of claim 7 , wherein the controller controls the compressor to operate at a slower speed in the cooling mode than in the heating mode.
19. The reversible heat pump system of claim 1 , wherein the load heat exchanger heats or cools potable water.
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Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10866002B2 (en) | 2016-11-09 | 2020-12-15 | Climate Master, Inc. | Hybrid heat pump with improved dehumidification |
US10871314B2 (en) | 2016-07-08 | 2020-12-22 | Climate Master, Inc. | Heat pump and water heater |
US10935260B2 (en) | 2017-12-12 | 2021-03-02 | Climate Master, Inc. | Heat pump with dehumidification |
US11480372B2 (en) | 2014-09-26 | 2022-10-25 | Waterfurnace International Inc. | Air conditioning system with vapor injection compressor |
US11506430B2 (en) | 2019-07-15 | 2022-11-22 | Climate Master, Inc. | Air conditioning system with capacity control and controlled hot water generation |
US11592215B2 (en) | 2018-08-29 | 2023-02-28 | Waterfurnace International, Inc. | Integrated demand water heating using a capacity modulated heat pump with desuperheater |
US11768018B2 (en) | 2021-05-03 | 2023-09-26 | Matthew Desmarais | Double hybrid heat pumps and systems and methods of use and operations |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6710061B2 (en) * | 2016-02-26 | 2020-06-17 | サンデン・オートモーティブクライメイトシステム株式会社 | Air conditioner for vehicle |
US11466911B2 (en) | 2016-11-30 | 2022-10-11 | Dc Engineering, Inc. | Method and system for improving refrigeration system efficiency |
US10760842B2 (en) * | 2016-11-30 | 2020-09-01 | Dc Engineering, Inc. | Method and system for improving refrigeration system efficiency |
US10830501B2 (en) * | 2018-04-25 | 2020-11-10 | Johnson Controls Technology Company | Systems for detecting and positioning of reversing valve |
US11919368B2 (en) * | 2021-10-07 | 2024-03-05 | Ford Global Technologies, Llc | Heat pump for a vehicle |
Citations (113)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4835976A (en) * | 1988-03-14 | 1989-06-06 | Eaton Corporation | Controlling superheat in a refrigeration system |
US5136855A (en) | 1991-03-05 | 1992-08-11 | Ontario Hydro | Heat pump having an accumulator with refrigerant level sensor |
US5224357A (en) | 1991-07-05 | 1993-07-06 | United States Power Corporation | Modular tube bundle heat exchanger and geothermal heat pump system |
US5461876A (en) | 1994-06-29 | 1995-10-31 | Dressler; William E. | Combined ambient-air and earth exchange heat pump system |
US5651265A (en) | 1994-07-15 | 1997-07-29 | Grenier; Michel A. | Ground source heat pump system |
US5758514A (en) | 1995-05-02 | 1998-06-02 | Envirotherm Heating & Cooling Systems, Inc. | Geothermal heat pump system |
US5927088A (en) * | 1996-02-27 | 1999-07-27 | Shaw; David N. | Boosted air source heat pump |
US6032472A (en) | 1995-12-06 | 2000-03-07 | Carrier Corporation | Motor cooling in a refrigeration system |
US6070423A (en) | 1998-10-08 | 2000-06-06 | Hebert; Thomas H. | Building exhaust and air conditioner condenstate (and/or other water source) evaporative refrigerant subcool/precool system and method therefor |
US6167715B1 (en) | 1998-10-06 | 2001-01-02 | Thomas H. Hebert | Direct refrigerant geothermal heat exchange or multiple source subcool/postheat/precool system therefor |
US6434960B1 (en) | 2001-07-02 | 2002-08-20 | Carrier Corporation | Variable speed drive chiller system |
US6474087B1 (en) | 2001-10-03 | 2002-11-05 | Carrier Corporation | Method and apparatus for the control of economizer circuit flow for optimum performance |
US6694750B1 (en) | 2002-08-21 | 2004-02-24 | Carrier Corporation | Refrigeration system employing multiple economizer circuits |
US6817205B1 (en) | 2003-10-24 | 2004-11-16 | Carrier Corporation | Dual reversing valves for economized heat pump |
US6857285B2 (en) | 1998-10-08 | 2005-02-22 | Global Energy Group, Inc. | Building exhaust and air conditioner condensate (and/or other water source) evaporative refrigerant subcool/precool system and method therefor |
US6892553B1 (en) | 2003-10-24 | 2005-05-17 | Carrier Corporation | Combined expansion device and four-way reversing valve in economized heat pumps |
US6931879B1 (en) | 2002-02-11 | 2005-08-23 | B. Ryland Wiggs | Closed loop direct expansion heating and cooling system with auxiliary refrigerant pump |
US6938438B2 (en) | 2003-04-21 | 2005-09-06 | Carrier Corporation | Vapor compression system with bypass/economizer circuits |
US6941770B1 (en) | 2004-07-15 | 2005-09-13 | Carrier Corporation | Hybrid reheat system with performance enhancement |
US20060010908A1 (en) * | 2004-07-15 | 2006-01-19 | Taras Michael F | Refrigerant systems with reheat and economizer |
US7000423B2 (en) | 2003-10-24 | 2006-02-21 | Carrier Corporation | Dual economizer heat exchangers for heat pump |
US7114349B2 (en) | 2004-12-10 | 2006-10-03 | Carrier Corporation | Refrigerant system with common economizer and liquid-suction heat exchanger |
US20060225445A1 (en) | 2005-04-07 | 2006-10-12 | Carrier Corporation | Refrigerant system with variable speed compressor in tandem compressor application |
US7150160B2 (en) | 1998-10-08 | 2006-12-19 | Global Energy Group, Inc. | Building exhaust and air conditioner condensate (and/or other water source) evaporative refrigerant subcool/precool system and method therefor |
US20070074536A1 (en) | 2002-11-11 | 2007-04-05 | Cheolho Bai | Refrigeration system with bypass subcooling and component size de-optimization |
US7228707B2 (en) | 2004-10-28 | 2007-06-12 | Carrier Corporation | Hybrid tandem compressor system with multiple evaporators and economizer circuit |
CN1987397A (en) | 2005-12-22 | 2007-06-27 | 乐金电子(天津)电器有限公司 | Method for detecting electronic expansion valve imperfect of composite air conditioner over cooling device |
US7272948B2 (en) | 2004-09-16 | 2007-09-25 | Carrier Corporation | Heat pump with reheat and economizer functions |
US7275385B2 (en) | 2005-08-22 | 2007-10-02 | Emerson Climate Technologies, Inc. | Compressor with vapor injection system |
US20070289319A1 (en) | 2006-06-16 | 2007-12-20 | In Kyu Kim | Geothermal air conditioning system |
US20070295477A1 (en) | 2005-11-14 | 2007-12-27 | Lynn Mueller | Geothermal Exchange System Using A Thermally Superconducting Medium With A Refrigerant Loop |
US20080016895A1 (en) | 2006-05-19 | 2008-01-24 | Lg Electronics Inc. | Air conditioning system using ground heat |
US7325414B2 (en) | 2004-10-28 | 2008-02-05 | Carrier Corporation | Hybrid tandem compressor system with economizer circuit and reheat function for multi-level cooling |
US20080173034A1 (en) * | 2007-01-19 | 2008-07-24 | Hallowell International, Llc | Heat pump apparatus and method |
US20080196418A1 (en) | 2005-06-06 | 2008-08-21 | Alexander Lifson | Method and Control for Preventing Flooded Starts in a Heat Pump |
US20080209930A1 (en) * | 2005-12-16 | 2008-09-04 | Taras Michael F | Heat Pump with Pulse Width Modulation Control |
EP1983275A1 (en) | 2007-04-17 | 2008-10-22 | Scroll Technologies | Refrigerant system with multi-speed scroll compressor and economizer circuit |
US20080256975A1 (en) | 2006-08-21 | 2008-10-23 | Carrier Corporation | Vapor Compression System With Condensate Intercooling Between Compression Stages |
US20080282718A1 (en) | 2005-12-01 | 2008-11-20 | Beagle Wayne P | Method and Apparatus of Optimizing the Cooling Load of an Economized Vapor Compression System |
US20080302129A1 (en) | 2006-08-01 | 2008-12-11 | Dieter Mosemann | Refrigeration system for transcritical operation with economizer and low-pressure receiver |
US20080307813A1 (en) | 2005-12-21 | 2008-12-18 | Carrier Corporation | Variable Capacity Multiple Circuit Air Conditioning System |
US7484374B2 (en) | 2006-03-20 | 2009-02-03 | Emerson Climate Technologies, Inc. | Flash tank design and control for heat pumps |
US20090208331A1 (en) | 2008-02-20 | 2009-08-20 | Haley Paul F | Centrifugal compressor assembly and method |
US7617697B2 (en) | 2006-05-16 | 2009-11-17 | Mccaughan Michael | In-ground geothermal heat pump system |
US20100005831A1 (en) | 2007-02-02 | 2010-01-14 | Carrier Corporation | Enhanced refrigerant system |
US7654104B2 (en) | 2005-05-27 | 2010-02-02 | Purdue Research Foundation | Heat pump system with multi-stage compression |
US20100024470A1 (en) | 2007-05-23 | 2010-02-04 | Alexander Lifson | Refrigerant injection above critical point in a transcritical refrigerant system |
US20100058781A1 (en) | 2006-12-26 | 2010-03-11 | Alexander Lifson | Refrigerant system with economizer, intercooler and multi-stage compressor |
US20100114384A1 (en) | 2008-10-28 | 2010-05-06 | Trak International, Llc | Controls for high-efficiency heat pumps |
US20100132399A1 (en) | 2007-04-24 | 2010-06-03 | Carrier Corporation | Transcritical refrigerant vapor compression system with charge management |
KR100963221B1 (en) | 2008-10-06 | 2010-06-10 | 강인구 | Heat pump system using terrestrial heat source |
US20100199715A1 (en) | 2007-09-24 | 2010-08-12 | Alexander Lifson | Refrigerant system with bypass line and dedicated economized flow compression chamber |
US20100251750A1 (en) | 2007-05-17 | 2010-10-07 | Carrier Corporation | Economized refrigerant system with flow control |
US20100281894A1 (en) | 2008-01-17 | 2010-11-11 | Carrier Corporation | Capacity modulation of refrigerant vapor compression system |
US20100287969A1 (en) | 2007-12-19 | 2010-11-18 | Mitsubishi Heavy Industries, Ltd. | Refrigerator |
US7845190B2 (en) | 2003-07-18 | 2010-12-07 | Star Refrigeration Limited | Transcritical refrigeration cycle |
US7854137B2 (en) | 2005-06-07 | 2010-12-21 | Carrier Corporation | Variable speed compressor motor control for low speed operation |
US7856834B2 (en) | 2008-02-20 | 2010-12-28 | Trane International Inc. | Centrifugal compressor assembly and method |
US20100326100A1 (en) | 2008-02-19 | 2010-12-30 | Carrier Corporation | Refrigerant vapor compression system |
US20110023515A1 (en) | 2009-07-31 | 2011-02-03 | Johnson Controls Technology Company | Refrigerant control system and method |
US20110036119A1 (en) * | 2008-05-02 | 2011-02-17 | Daikin Industries, Ltd. | Refrigeration apparatus |
US20110041523A1 (en) | 2008-05-14 | 2011-02-24 | Carrier Corporation | Charge management in refrigerant vapor compression systems |
US20110094248A1 (en) | 2007-12-20 | 2011-04-28 | Carrier Corporation | Refrigerant System and Method of Operating the Same |
US20110094259A1 (en) | 2007-10-10 | 2011-04-28 | Alexander Lifson | Multi-stage refrigerant system with different compressor types |
US20110132007A1 (en) | 2008-09-26 | 2011-06-09 | Carrier Corporation | Compressor discharge control on a transport refrigeration system |
US7975506B2 (en) | 2008-02-20 | 2011-07-12 | Trane International, Inc. | Coaxial economizer assembly and method |
US20110174014A1 (en) | 2008-10-01 | 2011-07-21 | Carrier Corporation | Liquid vapor separation in transcritical refrigerant cycle |
US7997092B2 (en) | 2007-09-26 | 2011-08-16 | Carrier Corporation | Refrigerant vapor compression system operating at or near zero load |
CN201944952U (en) | 2010-11-30 | 2011-08-24 | 深圳市英维克科技有限公司 | Air conditioner with subcooler |
US20110203299A1 (en) | 2008-11-11 | 2011-08-25 | Carrier Corporation | Heat pump system and method of operating |
US20110209490A1 (en) | 2008-10-31 | 2011-09-01 | Carrier Corporation | Control of multiple zone refrigerant vapor compression systems |
US8037713B2 (en) | 2008-02-20 | 2011-10-18 | Trane International, Inc. | Centrifugal compressor assembly and method |
US20110289950A1 (en) | 2010-05-28 | 2011-12-01 | Kim Byungsoon | Hot water supply apparatus associated with heat pump |
US8074459B2 (en) | 2006-04-20 | 2011-12-13 | Carrier Corporation | Heat pump system having auxiliary water heating and heat exchanger bypass |
US8079228B2 (en) | 2005-05-04 | 2011-12-20 | Scroll Technologies | Refrigerant system with multi-speed scroll compressor and economizer circuit |
US8079229B2 (en) | 2005-10-18 | 2011-12-20 | Carrier Corporation | Economized refrigerant vapor compression system for water heating |
US8082751B2 (en) | 2007-11-09 | 2011-12-27 | Earth To Air Systems, Llc | DX system with filtered suction line, low superheat, and oil provisions |
US20120011866A1 (en) | 2009-04-09 | 2012-01-19 | Carrier Corporation | Refrigerant vapor compression system with hot gas bypass |
CN102353126A (en) | 2011-09-09 | 2012-02-15 | 大连旺兴机电工程建设有限公司 | Air conditioning control system for air supply scroll compressor |
US8136364B2 (en) | 2006-09-18 | 2012-03-20 | Carrier Corporation | Refrigerant system with expansion device bypass |
US20120067965A1 (en) * | 2010-09-17 | 2012-03-22 | Hobart Brothers Company | Control systems and methods for modular heating, ventilating, air conditioning, and refrigeration systems |
US20120103005A1 (en) | 2010-11-01 | 2012-05-03 | Johnson Controls Technology Company | Screw chiller economizer system |
US8191376B2 (en) | 2009-06-18 | 2012-06-05 | Trane International Inc. | Valve and subcooler for storing refrigerant |
US8220531B2 (en) | 2005-06-03 | 2012-07-17 | Carrier Corporation | Heat pump system with auxiliary water heating |
US20120198867A1 (en) | 2009-10-14 | 2012-08-09 | Carrier Corporation | Dehumidification control in refrigerant vapor compression systems |
US20120247134A1 (en) | 2009-08-04 | 2012-10-04 | Echogen Power Systems, Llc | Heat pump with integral solar collector |
US20130031934A1 (en) | 2010-04-29 | 2013-02-07 | Carrier Corporation | Refrigerant vapor compression system with intercooler |
US8418486B2 (en) | 2005-04-08 | 2013-04-16 | Carrier Corporation | Refrigerant system with variable speed compressor and reheat function |
US8418482B2 (en) | 2006-03-27 | 2013-04-16 | Carrier Corporation | Refrigerating system with parallel staged economizer circuits using multistage compression |
US8424326B2 (en) | 2007-04-24 | 2013-04-23 | Carrier Corporation | Refrigerant vapor compression system and method of transcritical operation |
US20130098085A1 (en) | 2011-04-19 | 2013-04-25 | Liebert Corporation | High efficiency cooling system |
US8459052B2 (en) | 2006-09-29 | 2013-06-11 | Carrier Corporation | Refrigerant vapor compression system with flash tank receiver |
US20130180266A1 (en) | 2012-01-17 | 2013-07-18 | Schwab-Vollhaber-Lubratt, Inc. | Heat pump system |
US8528359B2 (en) | 2006-10-27 | 2013-09-10 | Carrier Corporation | Economized refrigeration cycle with expander |
CN203231582U (en) | 2013-04-11 | 2013-10-09 | 东华大学 | Two-stage compression heat pump system with economizer and defrosting by means of hot gas bypassing |
US20130269378A1 (en) * | 2012-04-17 | 2013-10-17 | Lee Wa Wong | Energy Efficient Air Heating, Air Conditioning and Water Heating System |
US8561425B2 (en) | 2007-04-24 | 2013-10-22 | Carrier Corporation | Refrigerant vapor compression system with dual economizer circuits |
US20130305756A1 (en) | 2012-05-21 | 2013-11-21 | Whirlpool Corporation | Synchronous temperature rate control and apparatus for refrigeration with reduced energy consumption |
CN103471275A (en) | 2013-08-30 | 2013-12-25 | 青岛海信日立空调系统有限公司 | Enhanced vapor injection air-conditioning circulating system and control method thereof |
CN203396155U (en) | 2013-06-17 | 2014-01-15 | 广东芬尼克兹节能设备有限公司 | Ultralow-temperature air source heat pump |
US20140013782A1 (en) * | 2010-09-14 | 2014-01-16 | Johnson Controls Technology Company | System and method for controlling an economizer circuit |
US20140013788A1 (en) | 2009-08-17 | 2014-01-16 | Johnson Controls Technology Company | Heat-pump chiller with improved heat recovery features |
US20140033753A1 (en) | 2011-04-19 | 2014-02-06 | Liebert Corporation | Load Estimator For Control Of Vapor Compression Cooling System With Pumped Refrigerant Economization |
US20140033755A1 (en) | 2012-08-06 | 2014-02-06 | Robert Hon-Sing Wong | Geothermal Rail Cooling and Heating System |
CN203432025U (en) | 2013-08-30 | 2014-02-12 | 海信(山东)空调有限公司 | Expansion valve ejection control system |
WO2014031559A1 (en) | 2012-08-24 | 2014-02-27 | Carrier Corporation | Transcritical refrigerant vapor compression system high side pressure control |
WO2014031708A1 (en) | 2012-08-24 | 2014-02-27 | Carrier Corporation | Stage transition in transcritical refrigerant vapor compression system |
US20140053585A1 (en) | 2011-04-21 | 2014-02-27 | Carrier Corporation | Transcritical Refrigerant Vapor System With Capacity Boost |
US20140060101A1 (en) | 2012-09-04 | 2014-03-06 | GM Global Technology Operations LLC | Unidirectional climate control system |
US8733429B2 (en) * | 2006-02-13 | 2014-05-27 | The H.L. Turner Group, Inc. | Hybrid heating and/or cooling system |
US8769982B2 (en) | 2006-10-02 | 2014-07-08 | Emerson Climate Technologies, Inc. | Injection system and method for refrigeration system compressor |
US20150059373A1 (en) * | 2013-09-05 | 2015-03-05 | Beckett Performance Products, Llc | Superheat and sub-cooling control of refrigeration system |
US20170227250A1 (en) * | 2002-03-06 | 2017-08-10 | John Chris Karamanos | Embedded heat exchanger with support mechanism |
Family Cites Families (409)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1723649A (en) | 1925-05-22 | 1929-08-06 | Heath Earl | Mounting for folding beds |
US3354774A (en) | 1964-06-01 | 1967-11-28 | Bell & Howell Co | Data abstract recording machines |
US3460353A (en) | 1967-11-07 | 1969-08-12 | Hitachi Ltd | Air conditioner |
US3916638A (en) | 1974-06-25 | 1975-11-04 | Weil Mclain Company Inc | Air conditioning system |
US3938352A (en) | 1974-07-10 | 1976-02-17 | Weil-Mclain Company, Inc. | Water to air heat pump employing an energy and condensate conservation system |
SE410512B (en) | 1976-02-03 | 1979-10-15 | Atomenergi Ab | HEAT PUMP DEVICE |
US4072187A (en) | 1976-05-10 | 1978-02-07 | Advance Machine Corporation | Compact heating and cooling system |
US4179894A (en) | 1977-12-28 | 1979-12-25 | Wylain, Inc. | Dual source heat pump |
US4173865A (en) | 1978-04-25 | 1979-11-13 | General Electric Company | Auxiliary coil arrangement |
US4257239A (en) | 1979-01-05 | 1981-03-24 | Partin James R | Earth coil heating and cooling system |
US4299098A (en) | 1980-07-10 | 1981-11-10 | The Trane Company | Refrigeration circuit for heat pump water heater and control therefor |
SE441303B (en) | 1981-03-20 | 1985-09-23 | Thermia Verken Ab | HEAD EXCHANGER WITH PARALLEL ROWS WITH RECTANGULATED SECTION WITH SPRING SPACES AT CERTAIN SPACES, WHICH USE AS DISTANCE ELEMENTS |
JPS57202462A (en) | 1981-06-05 | 1982-12-11 | Mitsubishi Electric Corp | Air conditioner |
US4399664A (en) | 1981-12-07 | 1983-08-23 | The Trane Company | Heat pump water heater circuit |
US4493193A (en) | 1982-03-05 | 1985-01-15 | Rutherford C. Lake, Jr. | Reversible cycle heating and cooling system |
US4476920A (en) | 1982-07-02 | 1984-10-16 | Carrier Corporation | Method and apparatus for integrating operation of a heat pump and a separate heating source |
DE3476577D1 (en) | 1983-08-10 | 1989-03-09 | Hitachi Ltd | Space cooling and heating and hot water supplying apparatus |
CA1193872A (en) * | 1983-09-20 | 1985-09-24 | Clayton Lemal | Heat pump |
CA1214336A (en) | 1983-10-11 | 1986-11-25 | Sven G. Oskarsson | Heat pump system |
KR900000809B1 (en) | 1984-02-09 | 1990-02-17 | 미쓰비시전기 주식회사 | Room-warming/cooling and hot-water supplying heat-pump apparatus |
US4538418A (en) | 1984-02-16 | 1985-09-03 | Demarco Energy Systems, Inc. | Heat pump |
US4909041A (en) | 1984-07-27 | 1990-03-20 | Uhr Corporation | Residential heating, cooling and energy management system |
US4645908A (en) | 1984-07-27 | 1987-02-24 | Uhr Corporation | Residential heating, cooling and energy management system |
US4685307A (en) | 1984-07-27 | 1987-08-11 | Uhr Corporation | Residential heating, cooling and energy management system |
US4528822A (en) | 1984-09-07 | 1985-07-16 | American-Standard Inc. | Heat pump refrigeration circuit with liquid heating capability |
US4798240A (en) * | 1985-03-18 | 1989-01-17 | Gas Research Institute | Integrated space heating, air conditioning and potable water heating appliance |
US4598557A (en) | 1985-09-27 | 1986-07-08 | Southern Company Services, Inc. | Integrated heat pump water heater |
US4646537A (en) | 1985-10-31 | 1987-03-03 | American Standard Inc. | Hot water heating and defrost in a heat pump circuit |
US4646538A (en) | 1986-02-10 | 1987-03-03 | Mississipi Power Co. | Triple integrated heat pump system |
US4693089A (en) | 1986-03-27 | 1987-09-15 | Phenix Heat Pump Systems, Inc. | Three function heat pump system |
US4776180A (en) | 1986-05-22 | 1988-10-11 | Mississippi Power Company | Updraft integrated heat pump |
AU591324B2 (en) | 1986-07-16 | 1989-11-30 | Graeme Clement Mudford | Air-conditioning system |
JPS6325471A (en) | 1986-07-17 | 1988-02-02 | 三菱電機株式会社 | Air conditioner |
US4698978A (en) | 1986-08-26 | 1987-10-13 | Uhr Corporation | Welded contact safety technique |
JP2504437B2 (en) | 1987-01-30 | 1996-06-05 | 株式会社東芝 | air conditioner |
US4727727A (en) | 1987-02-20 | 1988-03-01 | Electric Power Research Institute, Inc. | Integrated heat pump system |
US5463619A (en) | 1987-08-17 | 1995-10-31 | U.S. Philips Corporation | Local communication bus system comprising a set of interconnected devices, a control bus, and a set of signal interconnections, and a device and a switchbox for use in such system |
US4766734A (en) | 1987-09-08 | 1988-08-30 | Electric Power Research Institute, Inc. | Heat pump system with hot water defrost |
US4909312A (en) | 1987-09-18 | 1990-03-20 | Biedenbach Homer M | Interface equipment between a heat pump and a buried heat exchanger |
US4796437A (en) | 1987-10-23 | 1989-01-10 | James Larry S | Multifluid heat pump system |
US4856578A (en) | 1988-04-26 | 1989-08-15 | Nepco, Inc. | Multi-function self-contained heat pump system |
US4893476A (en) | 1988-08-12 | 1990-01-16 | Phenix Heat Pump Systems, Inc. | Three function heat pump system with one way receiver |
US4920757A (en) | 1988-08-18 | 1990-05-01 | Jimmy Gazes | Geothermal heating and air conditioning system |
JPH02150672A (en) | 1988-11-30 | 1990-06-08 | Toshiba Corp | Air-conditioner |
US4924681A (en) | 1989-05-18 | 1990-05-15 | Martin B. DeVit | Combined heat pump and domestic water heating circuit |
US5099651A (en) | 1989-09-05 | 1992-03-31 | Gas Research Institute | Gas engine driven heat pump method |
JP2801675B2 (en) | 1989-09-14 | 1998-09-21 | 株式会社東芝 | Air conditioner |
US5038580A (en) | 1989-12-05 | 1991-08-13 | Hart David P | Heat pump system |
US5081848A (en) | 1990-11-07 | 1992-01-21 | Rawlings John P | Ground source air conditioning system comprising a conduit array for de-icing a nearby surface |
US5105629A (en) | 1991-02-28 | 1992-04-21 | Parris Jesse W | Heat pump system |
US5172564A (en) | 1991-05-14 | 1992-12-22 | Electric Power Research Institute, Inc. | Integrated heat pump with restricted refrigerant feed |
US5269153A (en) | 1991-05-22 | 1993-12-14 | Artesian Building Systems, Inc. | Apparatus for controlling space heating and/or space cooling and water heating |
US5239838A (en) | 1991-09-19 | 1993-08-31 | Tressler Steven N | Heating and cooling system having auxiliary heating loop |
JPH05272829A (en) | 1992-03-25 | 1993-10-22 | Toshiba Corp | Air-conditioner |
US5309732A (en) | 1992-04-07 | 1994-05-10 | University Of Moncton | Combined cycle air/air heat pump |
US5187944A (en) | 1992-04-10 | 1993-02-23 | Eaton Corporation | Variable superheat target strategy for controlling an electrically operated refrigerant expansion valve |
JP3233447B2 (en) | 1992-06-02 | 2001-11-26 | 東芝キヤリア株式会社 | Air conditioner |
US5372016A (en) | 1993-02-08 | 1994-12-13 | Climate Master, Inc. | Ground source heat pump system comprising modular subterranean heat exchange units with multiple parallel secondary conduits |
US5339890A (en) | 1993-02-08 | 1994-08-23 | Climate Master, Inc. | Ground source heat pump system comprising modular subterranean heat exchange units with concentric conduits |
US5497629A (en) | 1993-03-23 | 1996-03-12 | Store Heat And Produce Energy, Inc. | Heating and cooling systems incorporating thermal storage |
US5355688A (en) | 1993-03-23 | 1994-10-18 | Shape, Inc. | Heat pump and air conditioning system incorporating thermal storage |
US5388419A (en) | 1993-04-23 | 1995-02-14 | Maritime Geothermal Ltd. | Staged cooling direct expansion geothermal heat pump |
US5438846A (en) | 1994-05-19 | 1995-08-08 | Datta; Chander | Heat-pump with sub-cooling heat exchanger |
US5465588A (en) | 1994-06-01 | 1995-11-14 | Hydro Delta Corporation | Multi-function self-contained heat pump system with microprocessor control |
US5619864A (en) | 1994-08-18 | 1997-04-15 | Nordyne, Inc. | Compact heat pump |
US5533355A (en) | 1994-11-07 | 1996-07-09 | Climate Master, Inc. | Subterranean heat exchange units comprising multiple secondary conduits and multi-tiered inlet and outlet manifolds |
US5729985A (en) | 1994-12-28 | 1998-03-24 | Yamaha Hatsudoki Kabushiki Kaisha | Air conditioning apparatus and method for air conditioning |
US5628200A (en) | 1995-01-12 | 1997-05-13 | Wallace Heating & Air Conditioning, Inc. | Heat pump system with selective space cooling |
US5613372A (en) | 1995-05-26 | 1997-03-25 | Dumont Management, Inc. | Heat pump system dehumidifier with secondary water loop |
US5706888A (en) | 1995-06-16 | 1998-01-13 | Geofurnace Systems, Inc. | Geothermal heat exchanger and heat pump circuit |
US6082125A (en) | 1996-02-23 | 2000-07-04 | Savtchenko; Peter | Heat pump energy management system |
US5689966A (en) | 1996-03-22 | 1997-11-25 | Battelle Memorial Institute | Method and apparatus for desuperheating refrigerant |
US5669224A (en) | 1996-06-27 | 1997-09-23 | Ontario Hydro | Direct expansion ground source heat pump |
US6123147A (en) | 1996-07-18 | 2000-09-26 | Pittman; Jerry R. | Humidity control apparatus for residential air conditioning system |
US6016629A (en) | 1996-10-25 | 2000-01-25 | Evenflo Company, Inc. | Walk-through gate |
US6000154A (en) | 1997-03-10 | 1999-12-14 | Clark Equipment Company | Quick change attachment for powered auxiliary tool |
US5802864A (en) | 1997-04-01 | 1998-09-08 | Peregrine Industries, Inc. | Heat transfer system |
CA2255181A1 (en) | 1997-12-02 | 1999-06-02 | Louis J. Bailey | Integrated system for heating, cooling and heat recovery ventilation |
US5937665A (en) | 1998-01-15 | 1999-08-17 | Geofurnace Systems, Inc. | Geothermal subcircuit for air conditioning unit |
US5983660A (en) | 1998-01-15 | 1999-11-16 | Geofurnace Systems, Inc. | Defrost subcircuit for air-to-air heat pump |
US5967411A (en) | 1998-01-23 | 1999-10-19 | Carrier Corporation | Method and apparatus for controlling supplemental heat in a heat pump system |
NO306797B1 (en) | 1998-03-24 | 1999-12-20 | Sakki Liv | Multifunctional air conditioning system, as well as method of multifunctional air conditioning |
JP3610812B2 (en) | 1998-07-01 | 2005-01-19 | ダイキン工業株式会社 | Refrigeration apparatus and refrigerant leak detection method |
US6212892B1 (en) | 1998-07-27 | 2001-04-10 | Alexander Pinkus Rafalovich | Air conditioner and heat pump with dehumidification |
JP2000046417A (en) | 1998-07-31 | 2000-02-18 | Daikin Ind Ltd | Heat pump type warm water floor heating apparatus |
US6705107B2 (en) | 1998-10-06 | 2004-03-16 | Manitowoc Foodservice Companies, Inc. | Compact ice making machine with cool vapor defrost |
JP3967033B2 (en) | 1999-03-19 | 2007-08-29 | 株式会社Nttファシリティーズ | Air conditioner and control method thereof |
JP2000314563A (en) | 1999-05-06 | 2000-11-14 | Hitachi Ltd | Air conditioner |
CN1156659C (en) | 1999-07-02 | 2004-07-07 | 华宏荪 | Thermodynamic equipment capable of regenerating energy sources |
AU768964B2 (en) | 1999-09-24 | 2004-01-08 | Peter Forrest Thompson | Heat pump fluid heating system |
US20020035845A1 (en) | 1999-10-22 | 2002-03-28 | David Smolinsky | Heating and refrigeration systems using refrigerant mass flow |
US6227003B1 (en) | 1999-10-22 | 2001-05-08 | David Smolinsky | Reverse-cycle heat pump system and device for improving cooling efficiency |
JP4345178B2 (en) | 2000-03-06 | 2009-10-14 | 株式会社富士通ゼネラル | Air conditioner |
WO2001090663A1 (en) | 2000-05-26 | 2001-11-29 | Thermal Energy Accumulator Products Pty Ltd | A multiple-use super-efficient heating and cooling system |
DE10029934A1 (en) | 2000-06-17 | 2002-01-03 | Behr Gmbh & Co | Air conditioning with air conditioning and heat pump mode |
JP3744330B2 (en) | 2000-09-26 | 2006-02-08 | ダイキン工業株式会社 | Air conditioner indoor unit |
CN1161570C (en) | 2000-09-26 | 2004-08-11 | 大金工业株式会社 | Air conditioner |
US6536221B2 (en) | 2001-01-16 | 2003-03-25 | Norbert L. James | Air conditioning heat recovery arrangement |
US6418745B1 (en) | 2001-03-21 | 2002-07-16 | Mechanical Solutions, Inc. | Heat powered heat pump system and method of making same |
US6615602B2 (en) | 2001-05-22 | 2003-09-09 | Ken Wilkinson | Heat pump with supplemental heat source |
CN1389689A (en) | 2001-06-01 | 2003-01-08 | 徐云生 | Peak-regulating ground source heat pump system for accumulating energy with valley power |
LU90841B1 (en) | 2001-09-25 | 2003-03-26 | Delphi Tech Inc | Combined heating and cooling system |
US6595012B2 (en) | 2001-09-29 | 2003-07-22 | Alexander P Rafalovich | Climate control system |
WO2003046440A1 (en) | 2001-11-30 | 2003-06-05 | Choon-Kyoung Park | Air conditioning apparatus |
US7155922B2 (en) | 2001-12-12 | 2007-01-02 | Quantum Energy Technologies Pty Limited | Energy efficient heat pump systems for water heating and air conditioning |
KR100473823B1 (en) | 2002-08-06 | 2005-03-08 | 삼성전자주식회사 | Air conditioner having cold and hot water supplying apparatus |
US6751972B1 (en) | 2002-11-18 | 2004-06-22 | Curtis A. Jungwirth | Apparatus for simultaneous heating cooling and humidity removal |
US6826921B1 (en) | 2003-07-03 | 2004-12-07 | Lennox Industries, Inc. | Air conditioning system with variable condenser reheat for enhanced dehumidification |
US6915656B2 (en) | 2003-07-14 | 2005-07-12 | Eco Technology Solutions, Llc | Heat pump system |
JP3858015B2 (en) | 2003-09-30 | 2006-12-13 | 三洋電機株式会社 | Refrigerant circuit and heat pump water heater |
US20050125083A1 (en) | 2003-11-10 | 2005-06-09 | Kiko Frederick J. | Automation apparatus and methods |
US7210303B2 (en) | 2003-12-04 | 2007-05-01 | Carrier Corporation | Transcritical heat pump water heating system using auxiliary electric heater |
US7716943B2 (en) | 2004-05-12 | 2010-05-18 | Electro Industries, Inc. | Heating/cooling system |
US7802441B2 (en) | 2004-05-12 | 2010-09-28 | Electro Industries, Inc. | Heat pump with accumulator at boost compressor output |
EP2535670B1 (en) | 2004-06-11 | 2014-08-06 | Daikin Industries, Ltd. | Air conditioner |
JP2006052934A (en) | 2004-07-12 | 2006-02-23 | Sanyo Electric Co Ltd | Heat exchange apparatus and refrigerating machine |
US20060218949A1 (en) | 2004-08-18 | 2006-10-05 | Ellis Daniel L | Water-cooled air conditioning system using condenser water regeneration for precise air reheat in dehumidifying mode |
US7275384B2 (en) | 2004-09-16 | 2007-10-02 | Carrier Corporation | Heat pump with reheat circuit |
US7770405B1 (en) | 2005-01-11 | 2010-08-10 | Ac Dc, Llc | Environmental air control system |
US7398778B2 (en) | 2005-01-24 | 2008-07-15 | Air Hydronic Product Solutions, Inc. | Solar and heat pump powered electric forced hot air hydronic furnace |
US7347059B2 (en) * | 2005-03-09 | 2008-03-25 | Kelix Heat Transfer Systems, Llc | Coaxial-flow heat transfer system employing a coaxial-flow heat transfer structure having a helically-arranged fin structure disposed along an outer flow channel for constantly rotating an aqueous-based heat transfer fluid flowing therewithin so as to improve heat transfer with geological environments |
CN100504256C (en) | 2005-03-28 | 2009-06-24 | 东芝开利株式会社 | Hot water supply device |
US7234311B2 (en) | 2005-04-04 | 2007-06-26 | Carrier Corporation | Prevention of compressor unpowered reverse rotation in heat pump units |
JP3963190B2 (en) | 2005-04-07 | 2007-08-22 | ダイキン工業株式会社 | Refrigerant amount determination system for air conditioner |
DE602005009152D1 (en) | 2005-05-10 | 2008-10-02 | Whirlpool Co | Method for producing a device housing |
JP3995007B2 (en) | 2005-05-30 | 2007-10-24 | ダイキン工業株式会社 | Humidity control device |
EP1886081A4 (en) | 2005-06-03 | 2011-06-08 | Carrier Corp | Refrigerant system with water heating |
KR20080022543A (en) | 2005-06-13 | 2008-03-11 | 스베닝 에릭슨 | Device and method for controlling cooling systems |
DE102005029048B4 (en) | 2005-06-21 | 2007-11-08 | Alfons Kruck | An air heat pump evaporator for an air heat pump heater and method of operating an air heat pump heater |
US7228696B2 (en) | 2005-06-27 | 2007-06-12 | Geofurnace Development Inc. | Hybrid heating and cooling system |
JP3915819B2 (en) | 2005-07-07 | 2007-05-16 | ダイキン工業株式会社 | Air conditioner |
US7263848B2 (en) | 2005-08-24 | 2007-09-04 | Delphi Technologies, Inc. | Heat pump system |
CA2616286A1 (en) | 2005-08-31 | 2007-03-08 | Carrier Corporation | Heat pump water heating system using variable speed compressor |
FR2894017B1 (en) | 2005-11-28 | 2008-02-15 | Financ Piscine Equipement Soc | HEAT PUMP FOR HEATING POOL WATER |
JP4124228B2 (en) | 2005-12-16 | 2008-07-23 | ダイキン工業株式会社 | Air conditioner |
JP3933179B1 (en) | 2005-12-16 | 2007-06-20 | ダイキン工業株式会社 | Air conditioner |
JP4120676B2 (en) | 2005-12-16 | 2008-07-16 | ダイキン工業株式会社 | Air conditioner |
JP2007163106A (en) | 2005-12-16 | 2007-06-28 | Daikin Ind Ltd | Air conditioner |
JP4114691B2 (en) | 2005-12-16 | 2008-07-09 | ダイキン工業株式会社 | Air conditioner |
US7265732B2 (en) | 2005-12-27 | 2007-09-04 | Ming-Tien Lin | Micro adjustable antenna bracket |
JP4165566B2 (en) | 2006-01-25 | 2008-10-15 | ダイキン工業株式会社 | Air conditioner |
JP4075933B2 (en) | 2006-01-30 | 2008-04-16 | ダイキン工業株式会社 | Air conditioner |
JP3963192B1 (en) | 2006-03-10 | 2007-08-22 | ダイキン工業株式会社 | Air conditioner |
JP4093275B2 (en) | 2006-03-20 | 2008-06-04 | ダイキン工業株式会社 | Air conditioner |
JP4705878B2 (en) | 2006-04-27 | 2011-06-22 | ダイキン工業株式会社 | Air conditioner |
JP4904908B2 (en) | 2006-04-28 | 2012-03-28 | ダイキン工業株式会社 | Air conditioner |
JP4155313B2 (en) | 2006-06-26 | 2008-09-24 | ダイキン工業株式会社 | Air conditioner |
US20100064710A1 (en) | 2006-07-10 | 2010-03-18 | James William Slaughter | Self contained water-to-water heat pump |
WO2008010798A1 (en) | 2006-07-19 | 2008-01-24 | Carrier Corporation | Refrigerant system with pulse width modulation for reheat circuit |
JP4169057B2 (en) | 2006-07-24 | 2008-10-22 | ダイキン工業株式会社 | Air conditioner |
JP5011957B2 (en) | 2006-09-07 | 2012-08-29 | ダイキン工業株式会社 | Air conditioner |
US8156757B2 (en) | 2006-10-06 | 2012-04-17 | Aff-Mcquay Inc. | High capacity chiller compressor |
ES2769383T3 (en) | 2006-10-13 | 2020-06-25 | Carrier Corp | Refrigeration circuit |
US20100024468A1 (en) | 2006-10-13 | 2010-02-04 | Carrier Corporation | Refrigeration unit comprising a micro channel heat exchanger |
JP4952210B2 (en) | 2006-11-21 | 2012-06-13 | ダイキン工業株式会社 | Air conditioner |
US7874499B2 (en) | 2006-11-22 | 2011-01-25 | Store-N-Stuff Llc | System and method to control sensible and latent heat in a storage unit |
US7823404B2 (en) | 2006-12-15 | 2010-11-02 | Lennox Industries Inc. | Air conditioning system with variable condenser reheat and refrigerant flow sequencer |
US8485789B2 (en) * | 2007-05-18 | 2013-07-16 | Emerson Climate Technologies, Inc. | Capacity modulated scroll compressor system and method |
WO2008148073A1 (en) | 2007-05-25 | 2008-12-04 | Hardin James R | Geothermal heat exchanger |
US20080302113A1 (en) | 2007-06-08 | 2008-12-11 | Jian-Min Yin | Refrigeration system having heat pump and multiple modes of operation |
DE102007050446C5 (en) | 2007-10-11 | 2017-08-31 | Steffen Karow | Indirectly evaporating heat pump and method for optimizing the inlet temperature of the indirectly evaporating heat pump |
US8161765B2 (en) | 2007-10-31 | 2012-04-24 | Thermodynamique Solutions Inc. | Heat exchange system with two single closed loops |
JP5326488B2 (en) | 2008-02-29 | 2013-10-30 | ダイキン工業株式会社 | Air conditioner |
JP5186951B2 (en) | 2008-02-29 | 2013-04-24 | ダイキン工業株式会社 | Air conditioner |
ES2799826T3 (en) | 2008-03-13 | 2020-12-21 | Daikin Applied Americas Inc | High capacity refrigerator compressor |
JP5103251B2 (en) | 2008-04-08 | 2012-12-19 | 日立アプライアンス株式会社 | Ceiling embedded heat source machine and air conditioner |
US20090294097A1 (en) | 2008-05-27 | 2009-12-03 | Rini Technologies, Inc. | Method and Apparatus for Heating or Cooling |
AU2013200092B2 (en) | 2008-06-27 | 2013-04-18 | Daikin Industries, Ltd | Air conditioning apparatus and air conditioning apparatus refrigerant quantity determination method |
JP2010007994A (en) | 2008-06-27 | 2010-01-14 | Daikin Ind Ltd | Air conditioning device and refrigerant amount determining method of air conditioner |
US8286438B2 (en) | 2008-07-03 | 2012-10-16 | Geosystems, Llc | System and method for controlling a refrigeration desuperheater |
JP2010038525A (en) | 2008-07-07 | 2010-02-18 | Daikin Ind Ltd | Coolant leak detection device and refrigeration device provided therewith |
WO2010005918A2 (en) | 2008-07-09 | 2010-01-14 | Carrier Corporation | Heat pump with microchannel heat exchangers as both outdoor and reheat heat exchangers |
US20100038052A1 (en) | 2008-07-16 | 2010-02-18 | Johnson James R | Geothermal hybrid heat exchange system |
US8312734B2 (en) | 2008-09-26 | 2012-11-20 | Lewis Donald C | Cascading air-source heat pump |
JP5040975B2 (en) | 2008-09-30 | 2012-10-03 | ダイキン工業株式会社 | Leakage diagnostic device |
JP2010101515A (en) | 2008-10-21 | 2010-05-06 | Daikin Ind Ltd | Refrigerant leakage detecting device and refrigerating device including the same |
JP2010101606A (en) | 2008-10-27 | 2010-05-06 | Daikin Ind Ltd | Refrigerant leakage detecting device and refrigerating device including the same |
US7975495B2 (en) | 2008-11-06 | 2011-07-12 | Trane International Inc. | Control scheme for coordinating variable capacity components of a refrigerant system |
US8695404B2 (en) | 2008-11-26 | 2014-04-15 | Delphi Technologies, Inc. | Refrigerant leak detection system |
JP2010133601A (en) | 2008-12-03 | 2010-06-17 | Daikin Ind Ltd | Refrigerant leakage detecting device and refrigerating unit having the same |
JP4975187B2 (en) | 2009-02-20 | 2012-07-11 | 三菱電機株式会社 | User side unit and air conditioner |
US8578724B2 (en) | 2009-03-13 | 2013-11-12 | Carrier Corporation | Heat pump and method of operation |
JP2010230181A (en) | 2009-03-25 | 2010-10-14 | Daikin Ind Ltd | Refrigerant leakage detection sensor |
JP5570531B2 (en) | 2010-01-26 | 2014-08-13 | 三菱電機株式会社 | Heat pump equipment |
KR101585943B1 (en) * | 2010-02-08 | 2016-01-18 | 삼성전자 주식회사 | Air conditioner and control method thereof |
KR101192346B1 (en) | 2010-04-22 | 2012-10-18 | 엘지전자 주식회사 | Heat pump type speed heating apparatus |
KR101175516B1 (en) | 2010-05-28 | 2012-08-23 | 엘지전자 주식회사 | Hot water supply device associated with heat pump |
US8910419B1 (en) | 2010-09-02 | 2014-12-16 | All Season Greens, LLC | Growing chamber |
US8598847B2 (en) | 2010-12-07 | 2013-12-03 | Volkswagen Ag | Balancing voltage for a multi-cell battery system |
US20130014451A1 (en) | 2011-01-14 | 2013-01-17 | Rodney Allen Russell | Prefabricated integrated utilities building core system |
US9851114B2 (en) | 2011-02-15 | 2017-12-26 | Trane International Inc. | HVAC system with multipurpose cabinet for auxiliary heat transfer components |
US8701432B1 (en) | 2011-03-21 | 2014-04-22 | Gaylord Olson | System and method of operation and control for a multi-source heat pump |
DE102012205200B4 (en) | 2011-04-04 | 2020-06-18 | Denso Corporation | Refrigerant cycle device |
US9052125B1 (en) | 2011-09-08 | 2015-06-09 | Dennis S. Dostal | Dual circuit heat pump |
US20170010029A9 (en) | 2011-09-23 | 2017-01-12 | R4 Ventures Llc | Multi Purpose Multistage Evaporative Cold Water and Cold Air Generating and Supply System |
US20130092329A1 (en) | 2011-10-13 | 2013-04-18 | All Access Staging & Productions, Inc. | Curtain sniffer |
US20130104574A1 (en) | 2011-11-02 | 2013-05-02 | Daniel J. Dempsey | Hybrid Space And Hot Water Heating Heat Pump |
US9383126B2 (en) | 2011-12-21 | 2016-07-05 | Nortek Global HVAC, LLC | Refrigerant charge management in a heat pump water heater |
US8756943B2 (en) | 2011-12-21 | 2014-06-24 | Nordyne Llc | Refrigerant charge management in a heat pump water heater |
US8726682B1 (en) | 2012-03-20 | 2014-05-20 | Gaylord Olson | Hybrid multi-mode heat pump system |
US20140123689A1 (en) | 2012-03-22 | 2014-05-08 | Climate Master, Inc. | Integrated heat pump and water heating circuit |
CH706507A1 (en) | 2012-05-14 | 2013-11-15 | Broder Ag | Coaxial borehole heat exchanger and method for assembling such a geothermal probe underground. |
JP2013250038A (en) | 2012-06-04 | 2013-12-12 | Daikin Industries Ltd | Refrigeration device management system |
CN104603557B (en) | 2012-08-27 | 2016-10-12 | 大金工业株式会社 | Refrigerating plant |
WO2014054178A1 (en) | 2012-10-05 | 2014-04-10 | 三菱電機株式会社 | Heat pump device |
WO2014054176A1 (en) | 2012-10-05 | 2014-04-10 | 三菱電機株式会社 | Heat pump device |
CN104884876B (en) | 2012-12-26 | 2017-03-08 | 三菱电机株式会社 | Refrigerating circulatory device and the control method of refrigerating circulatory device |
WO2014101225A1 (en) * | 2012-12-31 | 2014-07-03 | Trane International Inc. | Heat pump water heater |
US10072856B1 (en) | 2013-03-06 | 2018-09-11 | Auburn University | HVAC apparatus, method, and system |
US9389000B2 (en) | 2013-03-13 | 2016-07-12 | Rheem Manufacturing Company | Apparatus and methods for pre-heating water with air conditioning unit or heat pump |
FR3005150B1 (en) | 2013-04-24 | 2016-11-04 | Boostheat | METHOD AND DEVICE FOR INDICATING THE CONSUMPTION AND / OR EFFICIENCY OF A HEATING FACILITY |
JP6189098B2 (en) | 2013-06-14 | 2017-08-30 | 三菱重工オートモーティブサーマルシステムズ株式会社 | Heat pump air conditioning system for vehicles |
GB2515488B (en) | 2013-06-24 | 2016-09-21 | Airedale Int Air Conditioning Ltd | Air conditioner having angled heat exchangers |
CA2919507C (en) | 2013-07-12 | 2023-03-07 | John C. Karamanos | Fluid control measuring device |
US9297565B2 (en) | 2013-08-26 | 2016-03-29 | Lennox Industries Inc. | Charge management for air conditioning |
JP5812081B2 (en) | 2013-11-12 | 2015-11-11 | ダイキン工業株式会社 | Indoor unit |
JP2015094574A (en) | 2013-11-14 | 2015-05-18 | ダイキン工業株式会社 | Air conditioner |
US9797611B2 (en) | 2013-11-21 | 2017-10-24 | Atlas L.C. Heating & A/C | Combination air and ground source heating and/or cooling system |
US10401061B2 (en) | 2014-01-22 | 2019-09-03 | Desert Aire Corp. | Heat pump non-reversing valve arrangement |
JP6320060B2 (en) | 2014-01-31 | 2018-05-09 | 三菱電機株式会社 | Refrigeration cycle equipment |
JP6375639B2 (en) | 2014-02-21 | 2018-08-22 | ダイキン工業株式会社 | Air conditioner |
US20150252653A1 (en) | 2014-03-04 | 2015-09-10 | Geothermal Technologies, Inc. | System to enable geothermal field interaction with existing hvac systems, method to enable geothermal field interaction with existing hvac system |
JP2015175531A (en) | 2014-03-13 | 2015-10-05 | ダイキン工業株式会社 | Refrigeration device unit |
US9383026B2 (en) | 2014-03-19 | 2016-07-05 | Allen A. Eggleston | Method of repairing leaky HVAC service valves and an improved HVAC service valve which prevents leaks |
US10317112B2 (en) * | 2014-04-04 | 2019-06-11 | Johnson Controls Technology Company | Heat pump system with multiple operating modes |
US9879871B2 (en) | 2014-06-13 | 2018-01-30 | Lennox Industries Inc. | HVAC systems and methods with refrigerant leak detection |
US10119738B2 (en) | 2014-09-26 | 2018-11-06 | Waterfurnace International Inc. | Air conditioning system with vapor injection compressor |
JP6020534B2 (en) | 2014-10-31 | 2016-11-02 | ダイキン工業株式会社 | Air conditioner |
JP5939292B2 (en) | 2014-10-31 | 2016-06-22 | ダイキン工業株式会社 | Air conditioner |
JP5987887B2 (en) | 2014-10-31 | 2016-09-07 | ダイキン工業株式会社 | Air conditioner indoor unit |
JP6248898B2 (en) | 2014-10-31 | 2017-12-20 | ダイキン工業株式会社 | Air conditioner |
JP2016109356A (en) | 2014-12-05 | 2016-06-20 | ダイキン工業株式会社 | Air conditioner |
US10488065B2 (en) | 2014-12-17 | 2019-11-26 | Carrier Corporation | Leak detection unit for refrigerant system |
US10488072B2 (en) | 2015-02-18 | 2019-11-26 | Daikin Industries, Ltd. | Air conditioning system with leak protection control |
DE102015103681A1 (en) | 2015-03-13 | 2016-09-15 | Halla Visteon Climate Control Corporation | Air conditioning system of a motor vehicle and method for operating the air conditioning system |
JP6222252B2 (en) | 2015-03-30 | 2017-11-01 | ダイキン工業株式会社 | Air conditioner indoor unit |
WO2016158847A1 (en) | 2015-03-31 | 2016-10-06 | ダイキン工業株式会社 | Air conditioner |
JP6582496B2 (en) | 2015-03-31 | 2019-10-02 | ダイキン工業株式会社 | Air conditioning indoor unit |
JP6135705B2 (en) | 2015-04-06 | 2017-05-31 | ダイキン工業株式会社 | User side air conditioner |
US11079149B2 (en) | 2015-06-09 | 2021-08-03 | Carrier Corporation | System and method of diluting a leaked refrigerant in an HVAC/R system |
US10345004B1 (en) | 2015-09-01 | 2019-07-09 | Climate Master, Inc. | Integrated heat pump and water heating circuit |
US10151663B2 (en) | 2015-09-15 | 2018-12-11 | Emerson Climate Technologies, Inc. | Leak detector sensor systems using tag-sensitized refrigerants |
JP6623649B2 (en) | 2015-09-30 | 2019-12-25 | ダイキン工業株式会社 | Water heat exchanger storage unit |
JP2017075760A (en) | 2015-10-16 | 2017-04-20 | ダイキン工業株式会社 | Air conditioner |
KR101623746B1 (en) | 2015-11-05 | 2016-05-24 | 주식회사 제이앤지 | Second stage heating type geothermal heat system using geothermal energy |
US10633852B2 (en) | 2016-04-17 | 2020-04-28 | Majid Janabi | Reproducible building structure |
JP6876375B2 (en) | 2016-04-18 | 2021-05-26 | ダイキン工業株式会社 | Fan drive circuit of heat pump device |
US10871314B2 (en) | 2016-07-08 | 2020-12-22 | Climate Master, Inc. | Heat pump and water heater |
JP6428717B2 (en) | 2016-07-15 | 2018-11-28 | ダイキン工業株式会社 | Refrigeration system |
JP6304330B2 (en) | 2016-09-02 | 2018-04-04 | ダイキン工業株式会社 | Refrigeration equipment |
JP6269756B1 (en) | 2016-09-02 | 2018-01-31 | ダイキン工業株式会社 | Refrigeration equipment |
JP6337937B2 (en) | 2016-09-30 | 2018-06-06 | ダイキン工業株式会社 | Air conditioner |
JP6460073B2 (en) | 2016-09-30 | 2019-01-30 | ダイキン工業株式会社 | Air conditioner |
JP6380500B2 (en) | 2016-10-17 | 2018-08-29 | ダイキン工業株式会社 | Refrigeration equipment |
US10866002B2 (en) | 2016-11-09 | 2020-12-15 | Climate Master, Inc. | Hybrid heat pump with improved dehumidification |
WO2018123981A1 (en) | 2016-12-28 | 2018-07-05 | ダイキン工業株式会社 | Heat exchanger unit and air conditioner using same |
DE202017107917U1 (en) | 2016-12-30 | 2018-03-14 | Trane International Inc. | Refrigerant leakage detection by using a fluid additive |
JP7215819B2 (en) | 2017-01-11 | 2023-01-31 | ダイキン工業株式会社 | Air conditioner and indoor unit |
JP6798322B2 (en) | 2017-01-16 | 2020-12-09 | ダイキン工業株式会社 | Refrigeration equipment with shutoff valve |
KR101864636B1 (en) | 2017-01-17 | 2018-06-07 | 윤유빈 | Waste heat recovery type hybrid heat pump system |
CN110226073B (en) | 2017-02-09 | 2021-05-18 | 大金工业株式会社 | Refrigerating device |
EP3584521A4 (en) | 2017-02-14 | 2020-12-30 | Daikin Industries, Ltd. | Refrigerating device |
US11326798B2 (en) | 2017-02-23 | 2022-05-10 | Kenneth Ray Green | Refrigerant leak detection and mitigation system and method |
US11060775B2 (en) | 2017-03-09 | 2021-07-13 | Lennox Industries Inc. | Method and apparatus for refrigerant leak detection |
JP6555293B2 (en) | 2017-03-31 | 2019-08-07 | ダイキン工業株式会社 | Indoor unit of refrigeration equipment |
JP6477767B2 (en) | 2017-03-31 | 2019-03-06 | ダイキン工業株式会社 | Refrigeration equipment |
US10451297B2 (en) | 2017-05-01 | 2019-10-22 | Haier Us Appliance Solutions, Inc. | Air conditioning system including a reheat loop |
WO2018209350A1 (en) | 2017-05-12 | 2018-11-15 | Premium Home Comfort, Inc. | Air conditioner and an air conditioner housing |
AU2018310045B2 (en) | 2017-08-03 | 2021-04-29 | Daikin Industries, Ltd. | Refrigeration Apparatus |
DE202017105111U1 (en) | 2017-08-25 | 2017-09-08 | ATF Anwendungszentrum für Technik und Forschung UG (haftungsbeschränkt) | Heat recovery system and heat exchanger unit |
CN111033151A (en) | 2017-09-05 | 2020-04-17 | 大金工业株式会社 | Air conditioning system or refrigerant branching unit |
CN111094871B (en) | 2017-09-29 | 2021-09-17 | 大金工业株式会社 | Refrigerating device |
JP6935720B2 (en) | 2017-10-12 | 2021-09-15 | ダイキン工業株式会社 | Refrigeration equipment |
US10996131B2 (en) | 2017-12-01 | 2021-05-04 | Johnson Controls Technology Company | Refrigerant gas sensing system |
US20190170600A1 (en) | 2017-12-01 | 2019-06-06 | Johnson Controls Technology Company | Systems and methods for detecting refrigerant leaks in heating, ventilating, and air conditioning (hvac) systems |
US11573149B2 (en) | 2017-12-01 | 2023-02-07 | Johnson Controls Tyco IP Holdings LLP | Systems and methods for refrigerant leak management based on acoustic leak detection |
US10816247B2 (en) | 2017-12-01 | 2020-10-27 | Johnson Controls Technology Company | Heating, ventilation, and air conditioning control system |
US10684052B2 (en) | 2017-12-01 | 2020-06-16 | Johnson Controls Technology Company | Diagnostic mode of operation to detect refrigerant leaks in a refrigeration circuit |
US11231197B2 (en) | 2017-12-01 | 2022-01-25 | Johnson Controls Technology Company | Ultraviolet (UV) light-based refrigerant leak detection system and method |
US11060746B2 (en) | 2017-12-01 | 2021-07-13 | Johnson Controls Technology Company | Systems and methods for detecting and responding to refrigerant leaks in heating, ventilating, and air conditioning systems |
US10935454B2 (en) | 2017-12-01 | 2021-03-02 | Johnson Controls Technology Company | Systems and methods for refrigerant leak management |
US10677679B2 (en) | 2017-12-01 | 2020-06-09 | Johnson Controls Technology Company | Refrigerant leak detection and management based on condensation from air samples |
US10514176B2 (en) | 2017-12-01 | 2019-12-24 | Johnson Controls Technology Company | Systems and methods for refrigerant leak management |
US10935260B2 (en) | 2017-12-12 | 2021-03-02 | Climate Master, Inc. | Heat pump with dehumidification |
CN111479910A (en) | 2017-12-18 | 2020-07-31 | 大金工业株式会社 | Refrigerating machine oil for refrigerant or refrigerant composition, method for using refrigerating machine oil, and use as refrigerating machine oil |
JP7078840B2 (en) | 2018-01-19 | 2022-06-01 | ダイキン工業株式会社 | Heat exchanger and air conditioner |
JP7092987B2 (en) | 2018-01-22 | 2022-06-29 | ダイキン工業株式会社 | Indoor heat exchanger and air conditioner |
KR20190090972A (en) | 2018-01-26 | 2019-08-05 | 한국에너지기술연구원 | A Direct Refrigerant Circulation Heat Pump System Using Photovoltaic/Thermal and Geothermal. |
KR102552079B1 (en) | 2018-05-16 | 2023-07-06 | 현대자동차주식회사 | Roof on type air conditioner for vehicle and control method of the air conditioner |
JP7256248B2 (en) | 2018-05-21 | 2023-04-11 | 三菱電機株式会社 | Air conditioner packing set |
CN116804500A (en) | 2018-07-17 | 2023-09-26 | 大金工业株式会社 | Refrigeration cycle device |
US11898763B2 (en) | 2018-07-25 | 2024-02-13 | Daikin Industries, Ltd. | Air conditioning system with refrigerant leak management |
US11255588B2 (en) | 2018-08-03 | 2022-02-22 | Hoshizaki America, Inc. | Ultrasonic bin control in an ice machine |
US20210302051A1 (en) | 2018-08-06 | 2021-09-30 | Daikin Industries, Ltd. | Air conditioning system |
US11879650B2 (en) | 2018-08-06 | 2024-01-23 | Daikin Industries, Ltd. | Air conditioning system |
US20210293418A1 (en) | 2018-08-24 | 2021-09-23 | Fujitsu General Limited | Ceiling-embedded air conditioner |
US11592215B2 (en) | 2018-08-29 | 2023-02-28 | Waterfurnace International, Inc. | Integrated demand water heating using a capacity modulated heat pump with desuperheater |
US11946666B2 (en) | 2018-08-31 | 2024-04-02 | Daikin Industries, Ltd. | Air conditioner |
CN112840164B (en) | 2018-09-27 | 2023-01-17 | 大金工业株式会社 | Air conditioner and management device |
JP2020051738A (en) | 2018-09-28 | 2020-04-02 | ダイキン工業株式会社 | Heat load treatment system |
JP2020051735A (en) | 2018-09-28 | 2020-04-02 | ダイキン工業株式会社 | Heat exchange unit |
JP7157321B2 (en) | 2018-09-28 | 2022-10-20 | ダイキン工業株式会社 | Heat load handling system |
JP2020051736A (en) | 2018-09-28 | 2020-04-02 | ダイキン工業株式会社 | Heat load treatment system |
US10767882B2 (en) | 2018-10-17 | 2020-09-08 | Lennox Industries Inc. | Refrigerant pump down for an HVAC system |
US10941953B2 (en) | 2018-10-17 | 2021-03-09 | Lennox Industries Inc. | HVAC system and method of circulating flammable refrigerant |
US10731884B2 (en) | 2018-10-29 | 2020-08-04 | Johnson Controls Technology Company | Refrigerant leak management systems |
US11579601B2 (en) | 2019-01-15 | 2023-02-14 | Pricemy Developer LLC | Methods and devices for a building monitoring system |
US10816232B2 (en) | 2019-01-24 | 2020-10-27 | Lennox Industries Inc. | Systems and methods for pumping down flammable refrigerant |
JP6819706B2 (en) | 2019-01-31 | 2021-01-27 | ダイキン工業株式会社 | Refrigerant cycle device |
JP6750696B2 (en) | 2019-01-31 | 2020-09-02 | ダイキン工業株式会社 | Refrigerant cycle device |
JP7244744B2 (en) | 2019-02-13 | 2023-03-23 | ダイキン工業株式会社 | Equipment management system |
US11686491B2 (en) | 2019-02-20 | 2023-06-27 | Johnson Controls Tyco IP Holdings LLP | Systems for refrigerant leak detection and management |
US11098915B2 (en) | 2019-02-26 | 2021-08-24 | Lennox Industries Inc. | HVAC systems and methods with refrigerant purge |
JP2020143800A (en) | 2019-03-04 | 2020-09-10 | ダイキン工業株式会社 | Refrigerant cycle device |
ES2969543T3 (en) | 2019-03-05 | 2024-05-21 | Daikin Ind Ltd | air conditioning device |
JP7057510B2 (en) | 2019-06-14 | 2022-04-20 | ダイキン工業株式会社 | Refrigerant cycle device |
JP6849021B2 (en) | 2019-07-12 | 2021-03-24 | ダイキン工業株式会社 | Refrigeration cycle system |
CA3081986A1 (en) | 2019-07-15 | 2021-01-15 | Climate Master, Inc. | Air conditioning system with capacity control and controlled hot water generation |
AU2019464673B2 (en) | 2019-09-04 | 2023-11-02 | Daikin Europe N.V. | Compressor unit and refrigeration apparatus |
US20220307740A1 (en) | 2019-09-11 | 2022-09-29 | Carrier Corporation | System and method for mitigating risk from a leaked refrigerant at evaporator coils |
EP4028703A1 (en) | 2019-09-12 | 2022-07-20 | Carrier Corporation | Dual temperature sensor arrangement to detect refrigerant leak |
US20210207831A1 (en) | 2019-09-12 | 2021-07-08 | Carrier Corporation | Refrigerant leak detection and mitigation |
WO2021050617A1 (en) | 2019-09-13 | 2021-03-18 | Carrier Corporation | Hvac/r system with one or more leak mitigation dampers and method of diluting a leaked refrigerant in such a system |
WO2021054199A1 (en) | 2019-09-19 | 2021-03-25 | ダイキン工業株式会社 | Heat pump device |
US11408624B2 (en) | 2019-10-15 | 2022-08-09 | Carrier Corporation | Refrigerant leak detection |
EP3819553A3 (en) | 2019-11-06 | 2021-06-30 | Carrier Corporation | Redundant power supply for hvac system including refrigerant leakage mitigation |
JP2021085644A (en) | 2019-11-29 | 2021-06-03 | ダイキン工業株式会社 | Air conditioning system |
US11287153B2 (en) | 2019-12-02 | 2022-03-29 | Lennox Industries Inc. | Method and apparatus for risk reduction during refrigerant leak |
ES2966988T3 (en) | 2019-12-20 | 2024-04-25 | Daikin Europe Nv | Heat pump and method to install it |
JP2021103053A (en) | 2019-12-25 | 2021-07-15 | ダイキン工業株式会社 | Air conditioner |
US20210231330A1 (en) | 2020-01-23 | 2021-07-29 | My Mechanical Cloud, LLC | Monitor for hvac system |
JP2021135004A (en) | 2020-02-27 | 2021-09-13 | ダイキン工業株式会社 | Air conditioning system |
WO2021174076A1 (en) | 2020-02-28 | 2021-09-02 | Waterfurnace International, Inc. | Geothermal-ready heat pump system |
US11512867B2 (en) | 2020-03-12 | 2022-11-29 | Johnson Controls Tyco IP Holdings LLP | Refrigerant detection and control of HVAC system |
US20210293446A1 (en) | 2020-03-19 | 2021-09-23 | Carrier Corporation | Baffle for directing refrigerant leaks |
JP7037087B2 (en) | 2020-03-27 | 2022-03-16 | ダイキン工業株式会社 | Refrigeration cycle device |
US11428435B2 (en) | 2020-03-31 | 2022-08-30 | Johnson Controls Tyco IP Holdings LLP | Self-orienting refrigerant sensor systems |
EP3901526B1 (en) | 2020-04-24 | 2022-06-22 | Daikin Industries, Ltd. | Ceiling-mounted air conditioning unit for a heat pump comprising a refrigerant circuit with a refrigerant leakage sensor |
AU2020449188B2 (en) | 2020-05-20 | 2023-12-14 | Daikin Europe N.V. | Refrigeration cycle apparatus |
US11125457B1 (en) | 2020-07-16 | 2021-09-21 | Emerson Climate Technologies, Inc. | Refrigerant leak sensor and mitigation device and methods |
JP2022039608A (en) | 2020-08-28 | 2022-03-10 | ダイキン工業株式会社 | Air-conditioning system for computer rom |
JP6927397B1 (en) | 2020-09-24 | 2021-08-25 | ダイキン工業株式会社 | Air conditioning system and its indoor unit |
US11649997B2 (en) | 2020-09-29 | 2023-05-16 | Emerson Climate Technologies, Inc. | Refrigerant leak sensor power control systems and methods |
JP7189468B2 (en) | 2021-01-08 | 2022-12-14 | ダイキン工業株式会社 | Defect point estimation system, defect point estimation method, and program |
JP2021076368A (en) | 2021-01-27 | 2021-05-20 | ダイキン工業株式会社 | Heat pump device and valve kit |
EP4036486A1 (en) | 2021-01-29 | 2022-08-03 | Daikin Industries, Ltd. | Integrated hvac system for a building |
US11668483B2 (en) | 2021-02-01 | 2023-06-06 | Goodman Manufacturing Company LP | Systems and methods for air temperature control including A2L sensors |
US11662110B2 (en) | 2021-02-01 | 2023-05-30 | Goodman Manufacturing Company LP | Systems and methods for air temperature control including R-32 sensors |
US11909899B2 (en) | 2021-02-03 | 2024-02-20 | Motorola Mobility Llc | Hinged electronic device with displacement altering hinge and corresponding systems |
EP4310615A1 (en) | 2021-03-18 | 2024-01-24 | Daikin Industries, Ltd. | Correction device, prediction device, method, program, and correction model |
US11919362B2 (en) | 2021-04-30 | 2024-03-05 | Haier Us Appliance Solutions, Inc. | Noise reducing insert for an air conditioner unit |
US11578887B2 (en) | 2021-06-18 | 2023-02-14 | Lennox Industries Inc. | HVAC system leak detection |
US20230243539A1 (en) | 2021-08-31 | 2023-08-03 | Schneider Electric USA, Inc. | Monitoring hvac&r performance degradation using relative cop from joint power and temperature relations |
US20230097844A1 (en) | 2021-09-30 | 2023-03-30 | Carrier Corporation | Environmental enclosure for a transport gas sensor |
US20230094980A1 (en) | 2021-09-30 | 2023-03-30 | Carrier Corporation | Environmental enclosure for a transport gas sensor |
US20230106462A1 (en) | 2021-10-05 | 2023-04-06 | Carrier Corporation | Frost remidiation and frost sensor |
US20230109334A1 (en) | 2021-10-05 | 2023-04-06 | Emerson Climate Technologies, Inc. | Refrigerant Charge Monitoring Systems And Methods For Multiple Evaporators |
WO2023056617A1 (en) | 2021-10-09 | 2023-04-13 | Johnson Controls Tyco IP Holdings LLP | Systems and methods for controlling variable refrigerant flow systems using artificial intelligence |
US20230130167A1 (en) | 2021-10-21 | 2023-04-27 | Emerson Climate Technologies, Inc. | Climate control systems for use with high glide working fluids and methods for operation thereof |
JP2023071327A (en) | 2021-11-11 | 2023-05-23 | パナソニックIpマネジメント株式会社 | indoor unit |
WO2023084127A1 (en) | 2021-11-15 | 2023-05-19 | Maersk Container Industry A/S | Refrigeration system and method of determining a state of charge of refrigerant therein |
EP4194769A1 (en) | 2021-12-07 | 2023-06-14 | Glen Dimplex Deutschland GmbH | Refrigerant system and refrigerant module |
KR20230088078A (en) | 2021-12-10 | 2023-06-19 | 삼성전자주식회사 | Electronic apparatus and controlling method thereof |
JP2023098043A (en) | 2021-12-28 | 2023-07-10 | 三菱重工サーマルシステムズ株式会社 | Cut-off unit, air conditioner including the same, and vacuum drawing method |
JP7231866B1 (en) | 2021-12-28 | 2023-03-02 | ダイキン工業株式会社 | Anomaly detection device, method and program |
WO2023129777A1 (en) | 2021-12-30 | 2023-07-06 | Goodman Manufacturing Company, L.P. | System with leak detection for detecting refrigerant leak |
JP7332954B2 (en) | 2022-01-21 | 2023-08-24 | ダイキン工業株式会社 | Refrigerating device, refrigerant leak detection device, and refrigerant leakage detection method |
US20230235907A1 (en) | 2022-01-25 | 2023-07-27 | Johnson Controls Tyco IP Holdings LLP | Leakage detection and mitigation system |
JP2023119146A (en) | 2022-02-16 | 2023-08-28 | ダイキン工業株式会社 | air conditioning system |
JP7381944B2 (en) | 2022-02-16 | 2023-11-16 | ダイキン工業株式会社 | air conditioning system |
BE1030289B1 (en) | 2022-02-23 | 2023-09-18 | Daikin Europe Nv | METHOD FOR DETERMINING THE INTERNATIONAL LINKS BETWEEN SHUT-OFF VALVES AND REFRIGERANT LEAK SENSORS FOR AN AIR CONDITIONING SYSTEM |
BE1030293B1 (en) | 2022-02-23 | 2023-09-18 | Daikin Europe Nv | AIR CONDITIONING SYSTEM AND METHOD FOR ESTABLISHING A CONTROL LOGIC FOR OPERATING THE SHUT-OFF VALVE |
CN115435444A (en) | 2022-09-22 | 2022-12-06 | 青岛海尔空调器有限总公司 | Refrigerant detection method and device, electronic equipment and storage medium |
CN115468229A (en) | 2022-09-28 | 2022-12-13 | 海信空调有限公司 | Air conditioner |
CN115523604A (en) | 2022-10-11 | 2022-12-27 | 宁波奥克斯电气股份有限公司 | Multi-split-unit fault detection method and device and multi-split-unit |
CN115638523A (en) | 2022-10-14 | 2023-01-24 | 青岛海尔空调器有限总公司 | Air conditioner refrigerant leakage detection method and device and air conditioner |
KR102551286B1 (en) | 2022-10-21 | 2023-07-04 | (주)이엠티 | Refrigerator low pressure piping blockage inspection method |
KR102551281B1 (en) | 2022-10-21 | 2023-07-04 | (주)이엠티 | Refrigerator high pressure pipe blockage inspection method |
KR102551284B1 (en) | 2022-10-21 | 2023-07-04 | (주)이엠티 | Refrigerator low pressure piping blockage inspection method |
KR102569930B1 (en) | 2022-10-21 | 2023-08-23 | (주)이엠티 | Refrigerator Refrigeration Cycle Inspection Method |
CN218915295U (en) | 2022-10-28 | 2023-04-25 | 青岛海尔空调器有限总公司 | Sealing cover and air conditioner |
CN218511135U (en) | 2022-11-01 | 2023-02-21 | 叁九科技(杭州)有限公司 | Refrigerant leakage detection system in air conditioning system |
CN115493250A (en) | 2022-11-01 | 2022-12-20 | 叁九科技(杭州)有限公司 | Refrigerant leakage detection system in air conditioning system and control method thereof |
CN115930357A (en) | 2022-11-18 | 2023-04-07 | 青岛海尔空调器有限总公司 | Refrigerant leakage detection method of refrigerant circulation system and air conditioner using same |
CN115751508A (en) | 2022-11-23 | 2023-03-07 | 海信(广东)空调有限公司 | Dehumidifier and control method thereof |
CN115711454A (en) | 2022-11-24 | 2023-02-24 | 珠海格力电器股份有限公司 | Air conditioner control method, air conditioner and computer readable storage medium |
DE202022106612U1 (en) | 2022-11-25 | 2023-01-24 | Danfoss A/S | Encapsulation and heating, ventilating, and air conditioning system that includes the enclosure |
CN115854488A (en) | 2022-12-07 | 2023-03-28 | 青岛海信日立空调系统有限公司 | Air conditioning equipment and fault detection method |
CN115854484A (en) | 2022-12-09 | 2023-03-28 | 广东美的白色家电技术创新中心有限公司 | Refrigerant leakage detection method, device, system, equipment and storage medium |
CN218672483U (en) | 2022-12-12 | 2023-03-21 | 珠海格力电器股份有限公司 | Integrated air conditioning system |
CN116007066A (en) | 2022-12-12 | 2023-04-25 | 珠海格力电器股份有限公司 | Integrated air conditioning system and control method thereof |
CN115978709A (en) | 2022-12-15 | 2023-04-18 | 珠海格力电器股份有限公司 | Air conditioner refrigerant leakage determination method and device and air conditioner |
CN116123663A (en) | 2022-12-28 | 2023-05-16 | 海信(广东)空调有限公司 | Air conditioner |
CN116221902A (en) | 2022-12-30 | 2023-06-06 | 深圳市艾特网能技术有限公司 | Refrigerating device, data cabinet and control method thereof |
CN115978710A (en) | 2023-01-03 | 2023-04-18 | 珠海格力电器股份有限公司 | Plate heat exchanger leakage-proof control method and device, air conditioner and storage medium |
CN219415010U (en) | 2023-01-06 | 2023-07-25 | Tcl空调器(中山)有限公司 | Outdoor unit and air conditioner |
CN116085938A (en) | 2023-01-17 | 2023-05-09 | 广东美的暖通设备有限公司 | Refrigerant safety control device, air conditioner, method and medium |
CN116085939A (en) | 2023-01-17 | 2023-05-09 | 广东美的暖通设备有限公司 | Leakage detection control method, device, system, electrical appliance system and storage medium |
CN116025999A (en) | 2023-01-28 | 2023-04-28 | 宁波奥克斯电气股份有限公司 | Air conditioner and refrigerant leakage detection method |
ES2946857B2 (en) | 2023-01-30 | 2023-10-25 | Univ Valencia Politecnica | Refrigerant leak detection method and sensor |
CN116242010A (en) | 2023-02-20 | 2023-06-09 | 青岛海尔空调器有限总公司 | Method and device for detecting refrigerant leakage, air conditioner and storage medium |
CN116241979A (en) | 2023-03-16 | 2023-06-09 | 珠海格力电器股份有限公司 | Air conditioner control method and device, air conditioner and storage medium |
CN116294062A (en) | 2023-03-17 | 2023-06-23 | 青岛海尔空调器有限总公司 | Detection method and detection device for air conditioner refrigerant leakage and air conditioner |
CN116336607A (en) | 2023-03-27 | 2023-06-27 | 广东美的暖通设备有限公司 | Control method and device, electrical appliance system and computer readable storage medium |
CN219693510U (en) | 2023-03-31 | 2023-09-15 | 河南中烟工业有限责任公司 | Exhaust system of refrigerator room |
CN116294111A (en) | 2023-04-04 | 2023-06-23 | 珠海格力电器股份有限公司 | Air conditioner control method, air conditioner and computer storage medium |
CN116608539A (en) | 2023-04-13 | 2023-08-18 | 青岛海尔空调器有限总公司 | Dehumidifier and control method thereof |
CN116558042A (en) | 2023-05-05 | 2023-08-08 | 青岛海尔空调器有限总公司 | Detection method and device for air conditioner, air conditioner and storage medium |
CN116538638A (en) | 2023-05-23 | 2023-08-04 | 广东开利暖通空调股份有限公司 | Refrigerant leakage detection method and air conditioning system |
-
2015
- 2015-09-23 US US14/862,762 patent/US10119738B2/en active Active
-
2018
- 2018-10-03 US US16/150,821 patent/US10753661B2/en active Active
-
2020
- 2020-08-20 US US16/998,973 patent/US11480372B2/en active Active
-
2022
- 2022-10-11 US US18/045,774 patent/US11927377B2/en active Active
Patent Citations (116)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4835976A (en) * | 1988-03-14 | 1989-06-06 | Eaton Corporation | Controlling superheat in a refrigeration system |
US5136855A (en) | 1991-03-05 | 1992-08-11 | Ontario Hydro | Heat pump having an accumulator with refrigerant level sensor |
US5224357A (en) | 1991-07-05 | 1993-07-06 | United States Power Corporation | Modular tube bundle heat exchanger and geothermal heat pump system |
US5461876A (en) | 1994-06-29 | 1995-10-31 | Dressler; William E. | Combined ambient-air and earth exchange heat pump system |
US5651265A (en) | 1994-07-15 | 1997-07-29 | Grenier; Michel A. | Ground source heat pump system |
US5758514A (en) | 1995-05-02 | 1998-06-02 | Envirotherm Heating & Cooling Systems, Inc. | Geothermal heat pump system |
US6032472A (en) | 1995-12-06 | 2000-03-07 | Carrier Corporation | Motor cooling in a refrigeration system |
US5927088A (en) * | 1996-02-27 | 1999-07-27 | Shaw; David N. | Boosted air source heat pump |
US6167715B1 (en) | 1998-10-06 | 2001-01-02 | Thomas H. Hebert | Direct refrigerant geothermal heat exchange or multiple source subcool/postheat/precool system therefor |
US6070423A (en) | 1998-10-08 | 2000-06-06 | Hebert; Thomas H. | Building exhaust and air conditioner condenstate (and/or other water source) evaporative refrigerant subcool/precool system and method therefor |
US7150160B2 (en) | 1998-10-08 | 2006-12-19 | Global Energy Group, Inc. | Building exhaust and air conditioner condensate (and/or other water source) evaporative refrigerant subcool/precool system and method therefor |
US6857285B2 (en) | 1998-10-08 | 2005-02-22 | Global Energy Group, Inc. | Building exhaust and air conditioner condensate (and/or other water source) evaporative refrigerant subcool/precool system and method therefor |
US6434960B1 (en) | 2001-07-02 | 2002-08-20 | Carrier Corporation | Variable speed drive chiller system |
USRE39597E1 (en) | 2001-07-02 | 2007-05-01 | Carrier Corporation | Variable speed drive chiller system |
US6474087B1 (en) | 2001-10-03 | 2002-11-05 | Carrier Corporation | Method and apparatus for the control of economizer circuit flow for optimum performance |
US6931879B1 (en) | 2002-02-11 | 2005-08-23 | B. Ryland Wiggs | Closed loop direct expansion heating and cooling system with auxiliary refrigerant pump |
US20170227250A1 (en) * | 2002-03-06 | 2017-08-10 | John Chris Karamanos | Embedded heat exchanger with support mechanism |
US6694750B1 (en) | 2002-08-21 | 2004-02-24 | Carrier Corporation | Refrigeration system employing multiple economizer circuits |
US20070074536A1 (en) | 2002-11-11 | 2007-04-05 | Cheolho Bai | Refrigeration system with bypass subcooling and component size de-optimization |
US6938438B2 (en) | 2003-04-21 | 2005-09-06 | Carrier Corporation | Vapor compression system with bypass/economizer circuits |
US7845190B2 (en) | 2003-07-18 | 2010-12-07 | Star Refrigeration Limited | Transcritical refrigeration cycle |
US7000423B2 (en) | 2003-10-24 | 2006-02-21 | Carrier Corporation | Dual economizer heat exchangers for heat pump |
US6892553B1 (en) | 2003-10-24 | 2005-05-17 | Carrier Corporation | Combined expansion device and four-way reversing valve in economized heat pumps |
US6817205B1 (en) | 2003-10-24 | 2004-11-16 | Carrier Corporation | Dual reversing valves for economized heat pump |
US6941770B1 (en) | 2004-07-15 | 2005-09-13 | Carrier Corporation | Hybrid reheat system with performance enhancement |
US7059151B2 (en) | 2004-07-15 | 2006-06-13 | Carrier Corporation | Refrigerant systems with reheat and economizer |
US20060010908A1 (en) * | 2004-07-15 | 2006-01-19 | Taras Michael F | Refrigerant systems with reheat and economizer |
US7272948B2 (en) | 2004-09-16 | 2007-09-25 | Carrier Corporation | Heat pump with reheat and economizer functions |
US7325414B2 (en) | 2004-10-28 | 2008-02-05 | Carrier Corporation | Hybrid tandem compressor system with economizer circuit and reheat function for multi-level cooling |
US7228707B2 (en) | 2004-10-28 | 2007-06-12 | Carrier Corporation | Hybrid tandem compressor system with multiple evaporators and economizer circuit |
US7114349B2 (en) | 2004-12-10 | 2006-10-03 | Carrier Corporation | Refrigerant system with common economizer and liquid-suction heat exchanger |
US20060225445A1 (en) | 2005-04-07 | 2006-10-12 | Carrier Corporation | Refrigerant system with variable speed compressor in tandem compressor application |
US8418486B2 (en) | 2005-04-08 | 2013-04-16 | Carrier Corporation | Refrigerant system with variable speed compressor and reheat function |
US8079228B2 (en) | 2005-05-04 | 2011-12-20 | Scroll Technologies | Refrigerant system with multi-speed scroll compressor and economizer circuit |
US7654104B2 (en) | 2005-05-27 | 2010-02-02 | Purdue Research Foundation | Heat pump system with multi-stage compression |
US8220531B2 (en) | 2005-06-03 | 2012-07-17 | Carrier Corporation | Heat pump system with auxiliary water heating |
US7958737B2 (en) | 2005-06-06 | 2011-06-14 | Carrier Corporation | Method and control for preventing flooded starts in a heat pump |
US20080196418A1 (en) | 2005-06-06 | 2008-08-21 | Alexander Lifson | Method and Control for Preventing Flooded Starts in a Heat Pump |
US7854137B2 (en) | 2005-06-07 | 2010-12-21 | Carrier Corporation | Variable speed compressor motor control for low speed operation |
US7275385B2 (en) | 2005-08-22 | 2007-10-02 | Emerson Climate Technologies, Inc. | Compressor with vapor injection system |
US8079229B2 (en) | 2005-10-18 | 2011-12-20 | Carrier Corporation | Economized refrigerant vapor compression system for water heating |
US20070295477A1 (en) | 2005-11-14 | 2007-12-27 | Lynn Mueller | Geothermal Exchange System Using A Thermally Superconducting Medium With A Refrigerant Loop |
US20080282718A1 (en) | 2005-12-01 | 2008-11-20 | Beagle Wayne P | Method and Apparatus of Optimizing the Cooling Load of an Economized Vapor Compression System |
US20080209930A1 (en) * | 2005-12-16 | 2008-09-04 | Taras Michael F | Heat Pump with Pulse Width Modulation Control |
US20080307813A1 (en) | 2005-12-21 | 2008-12-18 | Carrier Corporation | Variable Capacity Multiple Circuit Air Conditioning System |
CN1987397A (en) | 2005-12-22 | 2007-06-27 | 乐金电子(天津)电器有限公司 | Method for detecting electronic expansion valve imperfect of composite air conditioner over cooling device |
US8733429B2 (en) * | 2006-02-13 | 2014-05-27 | The H.L. Turner Group, Inc. | Hybrid heating and/or cooling system |
US7484374B2 (en) | 2006-03-20 | 2009-02-03 | Emerson Climate Technologies, Inc. | Flash tank design and control for heat pumps |
US8418482B2 (en) | 2006-03-27 | 2013-04-16 | Carrier Corporation | Refrigerating system with parallel staged economizer circuits using multistage compression |
US8074459B2 (en) | 2006-04-20 | 2011-12-13 | Carrier Corporation | Heat pump system having auxiliary water heating and heat exchanger bypass |
US7617697B2 (en) | 2006-05-16 | 2009-11-17 | Mccaughan Michael | In-ground geothermal heat pump system |
US20080016895A1 (en) | 2006-05-19 | 2008-01-24 | Lg Electronics Inc. | Air conditioning system using ground heat |
US20070289319A1 (en) | 2006-06-16 | 2007-12-20 | In Kyu Kim | Geothermal air conditioning system |
US20080302129A1 (en) | 2006-08-01 | 2008-12-11 | Dieter Mosemann | Refrigeration system for transcritical operation with economizer and low-pressure receiver |
US20080256975A1 (en) | 2006-08-21 | 2008-10-23 | Carrier Corporation | Vapor Compression System With Condensate Intercooling Between Compression Stages |
US8136364B2 (en) | 2006-09-18 | 2012-03-20 | Carrier Corporation | Refrigerant system with expansion device bypass |
US8459052B2 (en) | 2006-09-29 | 2013-06-11 | Carrier Corporation | Refrigerant vapor compression system with flash tank receiver |
US8769982B2 (en) | 2006-10-02 | 2014-07-08 | Emerson Climate Technologies, Inc. | Injection system and method for refrigeration system compressor |
US8528359B2 (en) | 2006-10-27 | 2013-09-10 | Carrier Corporation | Economized refrigeration cycle with expander |
US20100058781A1 (en) | 2006-12-26 | 2010-03-11 | Alexander Lifson | Refrigerant system with economizer, intercooler and multi-stage compressor |
US20080173034A1 (en) * | 2007-01-19 | 2008-07-24 | Hallowell International, Llc | Heat pump apparatus and method |
US20100005831A1 (en) | 2007-02-02 | 2010-01-14 | Carrier Corporation | Enhanced refrigerant system |
EP1983275A1 (en) | 2007-04-17 | 2008-10-22 | Scroll Technologies | Refrigerant system with multi-speed scroll compressor and economizer circuit |
US8561425B2 (en) | 2007-04-24 | 2013-10-22 | Carrier Corporation | Refrigerant vapor compression system with dual economizer circuits |
US8424326B2 (en) | 2007-04-24 | 2013-04-23 | Carrier Corporation | Refrigerant vapor compression system and method of transcritical operation |
US20100132399A1 (en) | 2007-04-24 | 2010-06-03 | Carrier Corporation | Transcritical refrigerant vapor compression system with charge management |
US20100251750A1 (en) | 2007-05-17 | 2010-10-07 | Carrier Corporation | Economized refrigerant system with flow control |
US20100024470A1 (en) | 2007-05-23 | 2010-02-04 | Alexander Lifson | Refrigerant injection above critical point in a transcritical refrigerant system |
US20100199715A1 (en) | 2007-09-24 | 2010-08-12 | Alexander Lifson | Refrigerant system with bypass line and dedicated economized flow compression chamber |
US7997092B2 (en) | 2007-09-26 | 2011-08-16 | Carrier Corporation | Refrigerant vapor compression system operating at or near zero load |
US20110094259A1 (en) | 2007-10-10 | 2011-04-28 | Alexander Lifson | Multi-stage refrigerant system with different compressor types |
US8082751B2 (en) | 2007-11-09 | 2011-12-27 | Earth To Air Systems, Llc | DX system with filtered suction line, low superheat, and oil provisions |
US20100287969A1 (en) | 2007-12-19 | 2010-11-18 | Mitsubishi Heavy Industries, Ltd. | Refrigerator |
US20110094248A1 (en) | 2007-12-20 | 2011-04-28 | Carrier Corporation | Refrigerant System and Method of Operating the Same |
US20100281894A1 (en) | 2008-01-17 | 2010-11-11 | Carrier Corporation | Capacity modulation of refrigerant vapor compression system |
US20100326100A1 (en) | 2008-02-19 | 2010-12-30 | Carrier Corporation | Refrigerant vapor compression system |
US8037713B2 (en) | 2008-02-20 | 2011-10-18 | Trane International, Inc. | Centrifugal compressor assembly and method |
US7975506B2 (en) | 2008-02-20 | 2011-07-12 | Trane International, Inc. | Coaxial economizer assembly and method |
US20090208331A1 (en) | 2008-02-20 | 2009-08-20 | Haley Paul F | Centrifugal compressor assembly and method |
US7856834B2 (en) | 2008-02-20 | 2010-12-28 | Trane International Inc. | Centrifugal compressor assembly and method |
US20110036119A1 (en) * | 2008-05-02 | 2011-02-17 | Daikin Industries, Ltd. | Refrigeration apparatus |
US20110041523A1 (en) | 2008-05-14 | 2011-02-24 | Carrier Corporation | Charge management in refrigerant vapor compression systems |
US20110132007A1 (en) | 2008-09-26 | 2011-06-09 | Carrier Corporation | Compressor discharge control on a transport refrigeration system |
US20110174014A1 (en) | 2008-10-01 | 2011-07-21 | Carrier Corporation | Liquid vapor separation in transcritical refrigerant cycle |
KR100963221B1 (en) | 2008-10-06 | 2010-06-10 | 강인구 | Heat pump system using terrestrial heat source |
US20100114384A1 (en) | 2008-10-28 | 2010-05-06 | Trak International, Llc | Controls for high-efficiency heat pumps |
US20110209490A1 (en) | 2008-10-31 | 2011-09-01 | Carrier Corporation | Control of multiple zone refrigerant vapor compression systems |
US20110203299A1 (en) | 2008-11-11 | 2011-08-25 | Carrier Corporation | Heat pump system and method of operating |
US20120011866A1 (en) | 2009-04-09 | 2012-01-19 | Carrier Corporation | Refrigerant vapor compression system with hot gas bypass |
US8191376B2 (en) | 2009-06-18 | 2012-06-05 | Trane International Inc. | Valve and subcooler for storing refrigerant |
US20110023515A1 (en) | 2009-07-31 | 2011-02-03 | Johnson Controls Technology Company | Refrigerant control system and method |
US20120247134A1 (en) | 2009-08-04 | 2012-10-04 | Echogen Power Systems, Llc | Heat pump with integral solar collector |
US20140013788A1 (en) | 2009-08-17 | 2014-01-16 | Johnson Controls Technology Company | Heat-pump chiller with improved heat recovery features |
US20120198867A1 (en) | 2009-10-14 | 2012-08-09 | Carrier Corporation | Dehumidification control in refrigerant vapor compression systems |
US20130031934A1 (en) | 2010-04-29 | 2013-02-07 | Carrier Corporation | Refrigerant vapor compression system with intercooler |
US20110289950A1 (en) | 2010-05-28 | 2011-12-01 | Kim Byungsoon | Hot water supply apparatus associated with heat pump |
US20140013782A1 (en) * | 2010-09-14 | 2014-01-16 | Johnson Controls Technology Company | System and method for controlling an economizer circuit |
US20120067965A1 (en) * | 2010-09-17 | 2012-03-22 | Hobart Brothers Company | Control systems and methods for modular heating, ventilating, air conditioning, and refrigeration systems |
US20120103005A1 (en) | 2010-11-01 | 2012-05-03 | Johnson Controls Technology Company | Screw chiller economizer system |
CN201944952U (en) | 2010-11-30 | 2011-08-24 | 深圳市英维克科技有限公司 | Air conditioner with subcooler |
US20130098085A1 (en) | 2011-04-19 | 2013-04-25 | Liebert Corporation | High efficiency cooling system |
US20140033753A1 (en) | 2011-04-19 | 2014-02-06 | Liebert Corporation | Load Estimator For Control Of Vapor Compression Cooling System With Pumped Refrigerant Economization |
US20140053585A1 (en) | 2011-04-21 | 2014-02-27 | Carrier Corporation | Transcritical Refrigerant Vapor System With Capacity Boost |
CN102353126A (en) | 2011-09-09 | 2012-02-15 | 大连旺兴机电工程建设有限公司 | Air conditioning control system for air supply scroll compressor |
US20130180266A1 (en) | 2012-01-17 | 2013-07-18 | Schwab-Vollhaber-Lubratt, Inc. | Heat pump system |
US20130269378A1 (en) * | 2012-04-17 | 2013-10-17 | Lee Wa Wong | Energy Efficient Air Heating, Air Conditioning and Water Heating System |
US20130305756A1 (en) | 2012-05-21 | 2013-11-21 | Whirlpool Corporation | Synchronous temperature rate control and apparatus for refrigeration with reduced energy consumption |
US20140033755A1 (en) | 2012-08-06 | 2014-02-06 | Robert Hon-Sing Wong | Geothermal Rail Cooling and Heating System |
WO2014031708A1 (en) | 2012-08-24 | 2014-02-27 | Carrier Corporation | Stage transition in transcritical refrigerant vapor compression system |
WO2014031559A1 (en) | 2012-08-24 | 2014-02-27 | Carrier Corporation | Transcritical refrigerant vapor compression system high side pressure control |
US20140060101A1 (en) | 2012-09-04 | 2014-03-06 | GM Global Technology Operations LLC | Unidirectional climate control system |
CN203231582U (en) | 2013-04-11 | 2013-10-09 | 东华大学 | Two-stage compression heat pump system with economizer and defrosting by means of hot gas bypassing |
CN203396155U (en) | 2013-06-17 | 2014-01-15 | 广东芬尼克兹节能设备有限公司 | Ultralow-temperature air source heat pump |
CN203432025U (en) | 2013-08-30 | 2014-02-12 | 海信(山东)空调有限公司 | Expansion valve ejection control system |
CN103471275A (en) | 2013-08-30 | 2013-12-25 | 青岛海信日立空调系统有限公司 | Enhanced vapor injection air-conditioning circulating system and control method thereof |
US20150059373A1 (en) * | 2013-09-05 | 2015-03-05 | Beckett Performance Products, Llc | Superheat and sub-cooling control of refrigeration system |
Non-Patent Citations (13)
Title |
---|
134-XS and 134-S Series Compressors ECOnomizer (EA-12-03-E), 134-XS and 134-S series-Application and Maintenance Manual, Technical report EA1203E, RefComp Refrigerant Compressors, undated but believed to be publicly available at least as early as Mar. 2014 (4 pages). |
134-XS and 134-S Series Compressors ECOnomizer (EA-12-03-E), 134-XS and 134-S series—Application and Maintenance Manual, Technical report EA1203E, RefComp Refrigerant Compressors, undated but believed to be publicly available at least as early as Mar. 2014 (4 pages). |
B.P. Rasmussen et al., Model-Driven System Identification of Transcritical Vapor Compression Systems, IEEE Transactions on Control Systems Technology, May 2005, pp. 444-451, vol. 13 (8 pages). |
Economized Vapor Injection (EVI) Compressors, Emerson Climate Technologies Application Engineering Bulletin AE4-1327 R2, Revised Sep. 2006 (9 pages). |
Ekaterina Vinogradova, Economizers in Chiller Systems, Mikkelin Ammattikorkeakoulu, Nov. 2012 (50 pages). |
Enhanced Vapour Injection (EVI) for ZH*KVE Scroll Compressors, Emerson Climate Technologies-Technical Information C7.4.3/1107-0512/E, May 2012 (10 pages). |
Enhanced Vapour Injection (EVI) for ZH*KVE Scroll Compressors, Emerson Climate Technologies—Technical Information C7.4.3/1107-0512/E, May 2012 (10 pages). |
Henrik Haraldsson et al., Measurement of Performance and Evaluation of a Heat Pump-With Scroll Compressor EVI and Economizer, 2006 (4 pages). |
Henrik Haraldsson et al., Measurement of Performance and Evaluation of a Heat Pump—With Scroll Compressor EVI and Economizer, 2006 (4 pages). |
J. Lund et al., Geothermal (Ground-Source) Heat Pumps a World Overview, GHC Bulletin, Sep. 2004, (10 pages). |
John P. Elson et al., Scroll Technology: An Overview of Past, Present and Future Developments, International Compressor Engineering Conference, 2008, Paper 1871 (9 pages). |
Tolga N. Aynur, Variable Refrigerant Flow Systems: A Review, Energy and Buildings, Jan. 2010, pp. 1106-1112, vol. 42 (7 pages). |
Wei Yang et al., The Design Method of U-Bend Geothermal Heat Exchanger of DX-GCHP in Cooling Model, IEEE, 2011, pp. 3635-3637 (English Abstract) (3 pages). |
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US11480372B2 (en) | 2022-10-25 |
US20230055507A1 (en) | 2023-02-23 |
US10753661B2 (en) | 2020-08-25 |
US20160091236A1 (en) | 2016-03-31 |
US20200378667A1 (en) | 2020-12-03 |
US11927377B2 (en) | 2024-03-12 |
US20190032981A1 (en) | 2019-01-31 |
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